Hydraulic tool that commands prime mover output

ABSTRACT

The present disclosure provides embodiments directed towards a system for the control of hydraulic output by a hydraulic power source. In one embodiment, a system is provided. The system includes a hydraulic supply system having a drive, a hydraulic pump coupled to the drive, a first hydraulic output configured to supply a first flow of a hydraulic fluid from the hydraulic pump to a hydraulic lift, a second hydraulic output configured to supply a second flow of the hydraulic fluid from the hydraulic pump to a first hydraulic tool, and a controller configured to adjust a speed of the drive in response to a feedback indicative of a first load by the hydraulic lift, a second load by the first hydraulic tool, or a combination thereof.

CROSS REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional PatentApplication Ser. No. 61/368,362, entitled “HYDRAULIC TOOL THAT COMMANDSPRIME MOVER OUTPUT,” filed on Jul. 28, 2010, U.S. Provisional PatentApplication Ser. No. 61/368,369, entitled “HYDRAULIC TOOL THAT SWITCHESOUTPUT,” filed on Jul. 28, 2010, U.S. Provisional Patent ApplicationSer. No. 61/368,375, entitled “HYDRAULIC TOOL CONTROL WITHELECTRONICALLY ADJUSTABLE FLOW,” filed on Jul. 28, 2010, U.S.Provisional Patent Application Ser. No. 61/368,383, entitled “OPERATORINTERFACE FOR HYDRAULIC TOOL CONTROL,” filed on Jul. 28, 2010, all ofwhich are herein incorporated by reference in their entirety.

BACKGROUND

The present embodiments relate generally to power and flow managementfor an engine and a hydraulic pump used for powering hydraulic loads,such as hydraulic tools and/or cranes. More specifically, the presentdisclosure relates to the electronic control of engine speed andhydraulic fluid flow in a service pack or other unit capable ofproviding a flow of hydraulic fluid to hydraulic tools.

Some work vehicles may use one or more hydraulic-powered tools. Thesetools are powered via one or more pumps driven by an engine, such as thevehicle engine and/or an engine of a service pack. The one or more pumpsprovide a flow of hydraulic fluid to the hydraulic-powered tools forpower. In certain cases, the rate of flow of hydraulic fluid to a tooldetermines the amount of power available to the tool.

The main vehicle engine, which can power the one or more pumps and, insome configurations, other auxiliary devices, can be a large engine.Large engines are particularly noisy, and can be significantly overpowered for certain uses, causing them to be fuel inefficient in someinstances. Further, other smaller engines, such as the engine of aservice pack, can be fuel inefficient at times. For example, a typicalhydraulic system used to power a crane and other hydraulic tools may bepowered by an engine. Typically, the hydraulic system uses fullhydraulic output at full or idle engine speed, despite the amount ofload applied by the user. In such arrangements, there may either be toomuch power or too little power for the hydraulic tools. When there istoo much power, the user must make careful manual adjustments to avoidover-use or over-adjusting of the tool. Additionally, the use of fullengine and hydraulic output is often power-inefficient, which can reducethe life of the engine and hydraulic parts. When there is too littlepower, the user may not be able to utilize the full output of thehydraulic tools, and is only able to use one tool at a time. The carefulmanual adjustments may be difficult for the user, and can be inaccurate.Moreover, these manual adjustments to the hydraulic system and/or theengines are made at the system. Because some hydraulic tools may beconnected to the hydraulic system by long hydraulic lines, this mayresult in inefficiencies as the user walks back and forth from the workarea to the system. Accordingly, there is a need for improved systemsfor supplying hydraulic output to hydraulic loads, such as a crane andother hydraulic tools.

BRIEF DESCRIPTION

Certain aspects commensurate in scope with the originally claimedinvention are set forth below. It should be understood that theseaspects are presented merely to provide the reader with a brief summaryof certain forms the invention might take and that these aspects are notintended to limit the scope of the invention. Indeed, the invention mayencompass a variety of aspects that may not be set forth below.

The present embodiments address the above-mentioned and othershortcomings of hydraulic systems by providing embodiments directedtowards a method and a system for the electronic and/or automaticadjustment of hydraulic load output. In one embodiment, a system isprovided. The system includes a hydraulic supply system having a drive,a hydraulic pump coupled to the drive, a first hydraulic outputconfigured to supply a first flow of a hydraulic fluid from thehydraulic pump to a hydraulic lift, a second hydraulic output configuredto supply a second flow of the hydraulic fluid from the hydraulic pumpto a first hydraulic tool, and a controller configured to adjust a speedof the drive in response to a feedback indicative of a first load by thehydraulic lift, a second load by the first hydraulic tool, or acombination thereof.

In another embodiment, the present disclosure provides a system having acontroller configured to adjust a speed of a drive coupled to ahydraulic pump to change an output of the hydraulic pump. The controlleris configured to adjust the speed of the drive in response to a feedbackindicative of a first load by a hydraulic lift configured to receive afirst flow of hydraulic fluid from the hydraulic pump, a second load bya first hydraulic tool configured to receive a second flow of hydraulicfluid from the hydraulic pump, or a combination thereof.

In another embodiment, the present disclosure provides a system having aservice pack unit including a drive, a hydraulic pump coupled to thedrive, at least one hydraulic output configured to supply a hydraulicfluid from the hydraulic pump to at least one hydraulic tool, and acontroller configured to adjust a speed of the drive in response to afeedback indicative of a load by at least one hydraulic tool and atleast one relationship between the speed and the load.

In another embodiment, the present disclosure provides a system, havinga hydraulic supply system. The hydraulic supply system includes a drive,a hydraulic pump coupled to the drive, a first hydraulic outputconfigured to supply a first flow of a hydraulic fluid from thehydraulic pump to a hydraulic lift, a second hydraulic output configuredto supply a second flow of the hydraulic fluid from the hydraulic pumpto a first hydraulic tool, and a controller configured to switch betweena first mode and a second mode. The controller is configured to dedicatefirst and second flow rates to the respective first and second flows inthe first mode, and the controller is configured to dedicate third andfourth flow rates to the respective first and second flows in the secondmode.

In another embodiment, the present disclosure provides a system having ahydraulic tool control with a hydraulic input configured to couple to ahydraulic pump, a first hydraulic output configured to supply a firstflow of a hydraulic fluid from the hydraulic pump to a first hydraulictool, and a second hydraulic output configured to supply a second flowof the hydraulic fluid from the hydraulic pump to a second hydraulictool. The hydraulic tool control is configured to dedicate first andsecond flow rates to the respective first and second flows while thefirst hydraulic tool is in use.

In another embodiment, the present disclosure provides a system having ahydraulic supply system. The hydraulic supply system includes a drive, ahydraulic pump coupled to the drive, a first hydraulic output configuredto supply a first flow of a hydraulic fluid from the hydraulic pump to afirst hydraulic tool, a second hydraulic output configured to supply asecond flow of the hydraulic fluid from the hydraulic pump to a secondhydraulic tool, and a controller configured to dedicate first and secondflow rates to the respective first and second flows while the firsthydraulic tool is in use, and the controller is configured to supplementthe second flow while the first hydraulic tool is not in use.

In another embodiment, the present disclosure provides a system having ahydraulic supply system. The hydraulic supply system includes a drive, ahydraulic pump coupled to the drive, a first hydraulic output configuredto supply a first flow of a hydraulic fluid from the hydraulic pump,through a first electronically actuated valve, and to a hydraulic lift,and a second hydraulic output configured to supply a second flow of thehydraulic fluid from the hydraulic pump, through a second electronicallyactuated valve, and to a first hydraulic tool. The hydraulic supplysystem is configured to electronically adjust the first and secondelectronically actuated valves to adjust a first flow rate of the firstflow and a second flow rate of the second flow.

In another embodiment, the present disclosure provides a system having aservice pack unit. The service pack unit includes a drive, a hydraulicpump coupled to the drive, a first hydraulic output configured to supplya first flow of a hydraulic fluid from the hydraulic pump to a firsthydraulic tool, a second hydraulic output configured to supply a secondflow of the hydraulic fluid from the hydraulic pump to a secondhydraulic tool, and a hydraulic tool control comprising a controllercoupled to at least one electronically actuated valve, wherein thecontroller is configured to electronically adjust at least oneelectronically actuated valve to adjust a first flow rate of the firstflow or a second flow rate of the second flow.

In another embodiment, the present disclosure provides a system having ahydraulic tool control including a hydraulic input configured to coupleto a hydraulic pump, a first hydraulic output configured to supply afirst flow of a hydraulic fluid from the hydraulic pump, through a firstelectronically actuated valve, and to a first hydraulic tool. Thehydraulic tool control also includes a second hydraulic outputconfigured to supply a second flow of the hydraulic fluid from thehydraulic pump, through a second electronically actuated valve, and to asecond hydraulic tool. The hydraulic tool control is configured toelectronically adjust the first and second electronically actuatedvalves to adjust a first flow rate of the first flow and a second flowrate of the second flow.

In another embodiment, the present disclosure provides a system having aservice pack unit. The service pack unit includes a drive, a hydraulicpump coupled to the drive, a first hydraulic output configured to supplya first flow of a hydraulic fluid from the hydraulic pump to a firsthydraulic tool, a second hydraulic output configured to supply a secondflow of the hydraulic fluid from the hydraulic pump to a secondhydraulic tool, and a hydraulic tool control having at least oneelectronically actuated valve. The hydraulic tool control is configuredto electronically adjust at least one electronically actuated valve toadjust a first flow rate of the first flow or a second flow rate of thesecond flow.

In another embodiment, the present disclosure provides a system having ahydraulic supply system. The hydraulic supply system includes a drive, ahydraulic pump coupled to the drive, a first hydraulic output configuredto supply a first flow of a hydraulic fluid from the hydraulic pump to ahydraulic lift, a second hydraulic output configured to supply a secondflow of the hydraulic fluid from the hydraulic pump to a first hydraulictool, and a hydraulic tool control having an electronic user interface,a controller coupled to the electronic user interface, and at least oneelectronically actuated valve coupled to the controller, wherein theelectronic user interface has a display and an input device.

In another embodiment, the present disclosure provides a system having ahydraulic tool control including a hydraulic input configured to coupleto a hydraulic pump, a first hydraulic output configured to supply afirst flow of a hydraulic fluid from the hydraulic pump to a firsthydraulic tool, a second hydraulic output configured to supply a secondflow of the hydraulic fluid from the hydraulic pump to a secondhydraulic tool, an electronic user interface having a display and aninput device, and at least one electronically actuated valve configuredto adjust a first flow rate of the first flow or a second flow rate ofthe second flow. The input device is configured to enable the user toelectronically adjust a valve position of at least one electronicallyactuated valve.

In another embodiment, the present disclosure provides a system having aservice pack unit, including a drive, a hydraulic pump coupled to thedrive, a first hydraulic output configured to supply a first flow of ahydraulic fluid from the hydraulic pump to a first hydraulic tool, asecond hydraulic output configured to supply a second flow of thehydraulic fluid from the hydraulic pump to a second hydraulic tool, anda hydraulic tool control having at least one electronically actuatedvalve and an electronic user interface having a display and an inputdevice. The electronic user interface is configured to electronicallyadjust at least one electronically actuated valve to switch between aplurality of flow rates of the first and second flows.

DRAWINGS

These and other features, aspects, and advantages of the presentinvention will become better understood when the following detaileddescription is read with reference to the accompanying drawings in whichlike characters represent like parts throughout the drawings, wherein:

FIG. 1 is a diagram of an embodiment of a work vehicle having a servicepack with a hydraulic power source integrated with a hydraulic toolcontrol in accordance with the present embodiments;

FIG. 2 is a diagram of an embodiment of power systems in the vehicle ofFIG. 1, illustrating support systems of the service pack separate andindependent from support systems of a vehicle engine;

FIG. 3 is a diagram of an embodiment of power systems in the vehicle ofFIG. 1, illustrating support systems of the service pack integrated withsupport systems of the vehicle engine;

FIGS. 4A-4C are diagrams of embodiments of the service pack withdifferent arrangements of a generator, a hydraulic pump, and an aircompressor driven by a service pack engine in accordance with thepresent disclosure;

FIG. 5 is an illustration of an embodiment of the service pack of FIG. 1in operative connection with a hydraulic reservoir and hydraulic toolcontrol in accordance with the present disclosure;

FIG. 6 is a perspective view of an embodiment of the hydraulic toolcontrol of FIG. 5 having hydraulic connections for connecting to aplurality of hydraulic tools and an electronic user interface inaccordance with the present disclosure;

FIG. 7 is a plan view of one side of the hydraulic tool control of FIG.6 having hydraulic connections for connecting to a heat exchanger and anauxiliary hydraulic tool and communication connections for communicatingwith a service pack and a service pack remote panel in accordance withthe present disclosure;

FIG. 8 is a block diagram illustrating an embodiment of a hydraulicsystem having a prime mover, a hydraulic power source, a hydraulic toolcontrol, and a plurality of hydraulic tools connected to the hydraulictool control in accordance with the present disclosure;

FIG. 9 is a circuit diagram depicting one embodiment of a hydraulicsystem having a variable displacement pump in operative connection witha hydraulic tool control and a plurality of hydraulic tool circuitsconnected to the hydraulic tool control in accordance with the presentdisclosure;

FIG. 10 is a circuit diagram depicting one embodiment of a hydraulicsystem having a fixed displacement pump in operative connection with thehydraulic tool control and plurality of hydraulic tool circuitsconnected to the hydraulic tool control of FIG. 9 in accordance with thepresent disclosure;

FIG. 11 is a process flow diagram illustrating one embodiment of amethod for adjusting prime mover output based on a sensed demand forhydraulic fluid in accordance with the present disclosure;

FIG. 12 is a process flow diagram illustrating one embodiment of amethod for controlling hydraulic output with a hydraulic tool control inaccordance with the present disclosure;

FIG. 13 is a process flow diagram illustrating one embodiment of amethod for controlling hydraulic output with a hydraulic tool controlwhile the hydraulic tool control is providing hydraulic fluid to aprimary and a secondary hydraulic tool in accordance with the presentdisclosure;

FIG. 14 is a process flow diagram illustrating one embodiment of amethod for controlling hydraulic output with a hydraulic tool controlwhile the hydraulic tool control is providing hydraulic fluid to aprimary and an auxiliary hydraulic tool in accordance with the presentdisclosure;

FIG. 15 is a front view of an embodiment of a faceplate for use inconjunction with a hydraulic tool control, the faceplate havingconnection covers, various indicators for indicating operational modes,and electronic controls that enable a user to electronically switchbetween the various operational modes of the hydraulic tool control inaccordance with the present disclosure;

FIG. 16 is a front view of an embodiment of a faceplate for use inconjunction with a hydraulic tool control, the faceplate havingconnection covers, various indicators for indicating operational modes,and electronic controls that enable a user to electronically switchbetween the various operational modes of the hydraulic tool control inaccordance with the present disclosure;

FIG. 17 is a front view of an embodiment of a faceplate for use inconjunction with a hydraulic tool control, the faceplate havingconnection covers, various indicators for indicating operational modes,and electronic controls that enable a user to electronically switchbetween the various operational modes of the hydraulic tool control inaccordance with the present disclosure;

FIG. 18 is a front view of an embodiment of a faceplate for use inconjunction with a hydraulic tool control, the faceplate havingconnection covers, various indicators for indicating operational modes,and electronic controls that enable a user to electronically switchbetween the various operational modes of the hydraulic tool control inaccordance with the present disclosure; and

FIG. 19 is a front view of an embodiment of a user interface for use inconjunction with a hydraulic tool and a hydraulic tool controloperatively connected to the hydraulic tool, the user interface havingvarious indicators for indicating operational modes of the hydraulictool control, and electronic controls that enable a user toelectronically switch between the various operational modes of thehydraulic tool control in accordance with the present disclosure.

DETAILED DESCRIPTION

As discussed below, the present disclosure provides a uniquely effectivesolution to the control of hydraulic output in various applications.Thus, the disclosed embodiments relate or deal with any applicationwhere a prime mover or power source that is engine driven intermittentlypowers a hydraulic load or a combination of hydraulic loads. In certainembodiments, the disclosed hydraulic output control techniques may beused with various service packs and/or hydraulic pumps to preventunnecessary or wasteful use of (and exhaust emissions by) a power sourcethat is coupled to multiple loads, specifically one or more hydraulicloads. The present disclosure also provides embodiments that allow theuse of multiple hydraulic tools simultaneously. For example, thedisclosed embodiments may be used in combination with any and all of theembodiments set forth in U.S. application Ser. No. 11/742,399, filed onApr. 30, 2007, and entitled “ENGINE-DRIVEN AIR COMPRESSOR/GENERATOR LOADPRIORITY CONTROL SYSTEM AND METHOD,” which is hereby incorporated byreference in its entirety. By further example, the disclosed embodimentsmay be used in combination with any and all of the embodiments set forthin U.S. application Ser. No. 11/943,564, filed on Nov. 20, 2007, andentitled “AUXILIARY SERVICE PACK FOR A WORK VEHICLE,” which is herebyincorporated by reference in its entirety.

As discussed below, the present embodiments may utilize any one or acombination of user input, hydraulic load sensing, load sensing from theactivation of a trigger, or any load sensing to determine an amount ofhydraulic output suitable for a given task. The hydraulic output may becontrolled by a hydraulic tool control (HTC), which can interface withor include a controller for adjusting the speed of an engine driving oneor more hydraulic pumps. Additionally or alternatively, a user mayselect from various flow schemes for the HTC, such as certain flow modesthat determine the flow rate of hydraulic fluid delivered to one or morehydraulic tools. The user may perform this selection manually on anelectronic interface of the HTC, or the selection may be performedautomatically by a controller, integrated with or otherwise operativelycoupled to the HTC, via load sensing. Depending on the flow scheme thatis selected, the HTC may provide a hydraulic output to one hydraulicload, such as a crane or impact wrench, or may provide a usablehydraulic output to multiple hydraulic loads, such as the crane and theimpact wrench, or the impact wrench and another hydraulic tool. Further,the HTC may automatically select a suitable amount of hydraulic outputdepending on an amount of hydraulic load demanded by each tool. Forexample, the HTC may substantially match the hydraulic output (e.g.,supply) to the hydraulic demand by one or more hydraulic tools, e.g.,based on various sensor feedback indicative of the load (i.e., a loadsense). In particular, the HTC may adjust the engine speed, e.g., viaelectronic control, continuously or incrementally in proportion to thedemand for hydraulic power by one or more hydraulic tools, therebyreducing the possibility of the engine running too fast or too slow forthe particular hydraulic demand. To allow the HTC to perform such tasks,the system having the HTC may include a service pack having an engine.The engine is generally coupled to a hydraulic pump, which provides theflow of hydraulic fluid to the hydraulic tools.

Keeping in mind that the present embodiments relate to hydraulic outputfor a variety of different hydraulic systems, the present disclosurewill discuss the present embodiments in the context of a service packintegral with or mounted to a work vehicle. One embodiment of such awork vehicle 10 is depicted in FIG. 1. The work vehicle 10 is shown as awork truck, although the work vehicle 10 may have any other suitableconfiguration. In the illustrated embodiment, the vehicle 10 includes aservice pack 12 for supplying various services (e.g., electrical,compressed air, and hydraulic power) to a range of applications 14. Asdiscussed in further detail below, the service pack 12 includes ahydraulic tool control (HTC) 16 configured to control hydraulic outputto one or more hydraulic loads. The vehicle 10 has a main vehicle powerplant 18 based around a vehicle engine 20. The main vehicle engine 20may include a spark ignition engine (e.g., gasoline fueled internalcombustion engine) or a compression ignition engine (e.g., a dieselfueled engine).

The vehicle power plant 18 includes a number of support systems. Forexample, the engine 20 consumes fuel from a fuel reservoir 22, e.g., oneor more liquid fuel tanks. An air intake or air cleaning system 24supplies air to engine 20, which may, in some applications, be turbocharged or super charged. A cooling system 26, e.g., a radiator,circulation pump, a thermostat-controlled valve and a fan, provides forcooling the engine 20. The vehicle power plant 18 also includes anelectrical system 28, which may include an alternator or generator,along with one or more system batteries 30. The vehicle power plant 18also includes a lube oil system 32 and an exhaust system 34.

The service pack 12 may include one or more service systems driven by aservice engine 36. Generally, the service pack 12 provides electricalpower, hydraulic power, and compressed air for the applications 14. Inthe diagrammatical representation of FIG. 1, for example, the serviceengine 36 drives a generator 38 as well as a hydraulic pump 40 and aircompressor 42. The hydraulic pump 40 may be based on any suitabletechnology, such as piston pumps, gear pumps, vane pumps, with orwithout closed-loop control of pressure and/or flow. In certainembodiments, the pump 40 may include a constant displacement pump, avariable displacement pump, a plurality of pumps in a parallel or seriesconfiguration, or a combination thereof. As discussed in detail below,the HTC 16, which may be in communication with the service pack 12, maymonitor the application of hydraulic loads (e.g., via trigger position,pressure drops, or the like). In response to the load, the HTC 16 mayadjust the output of the main vehicle engine 20, the service engine 36,and/or the hydraulic pump 40. For example, in order to providesufficient power and/or control for an applied hydraulic load, the HTC16, in some embodiments, functions to adjust the speed of the engine 20,the engine 36, and/or the position of one or more valves that controlthe level of output of the hydraulic pump 40 to a plurality of hydraulictools.

Like the hydraulic pump 40, the generator 38 may be directly driven bythe engine 36 rather than engine 20. For example, the generator 38 maybe close coupled to the engine 36, or may be belt or chain driven, wheredesired. The air compressor 42 may be of any suitable type, such as arotary screw air compressor or a reciprocating piston air compressor. Ofcourse, the systems of the service pack 12 include appropriate conduits,wiring, tubing and so forth for conveying the service generated by thesecomponents to an access point, and for control by a control system.Convenient access points will be located around the periphery of thevehicle, such as access to the HTC 16 that enables a user to easily makechanges to hydraulic output as desired. In one embodiment, the generatorand compressor services may be routed to a common access point, whilethe hydraulic service is routed through the HTC 16. For example, thediagrammatical view of FIG. 1 illustrates the generator 38 as coupled toelectrical cabling 44 (for AC power supply) and 46 (for 12 volt DC powersupply). The hydraulic pump 40 is coupled to hydraulic circuit 47 andthe air compressor 42 is coupled to an air circuit 48.

As represented generally in FIG. 1, the generator 38 is also coupled tothe vehicle electrical system, and particularly to the vehicle battery30. Thus, not only may the service pack 12 allow for 12 volt loads to bepowered without operation of the main vehicle engine 20, but the vehiclebattery 30 may serve as a shared battery, and is maintained in a stateof charge by the service pack 12 generator output. In certainembodiments, a control system may monitor the level of charge of thevehicle battery 30 to ensure substantially continuous operation of theHTC 16, monitoring of applied loads, power consumption, and so forth.

The cabling and conduits 44, 46, 47, 48 may, as in the illustratedembodiment, route service for all of these systems directly fromconnections on the service pack 12. Accordingly, certain controlfunctions, such as control of certain compressor and/or generatoroperations, may be available from a control and service panel 50. Thepanel 50 may also enable certain engine parameters to be monitored, suchas the speed of the service engine 36, the speed of the vehicle engine20, the output of the generator 38 and/or compressor 42, and so on. Theservice panel 50 may be located on any surface of the vehicle 10, or onmultiple locations in the vehicle 10. The control and access panel 50,in some embodiments, may be in communication with the HTC 16. In asimilar manner to the circuits 44, 46, and 48, the hydraulic circuit 47is routed to the HTC 16. The HTC 16 enables functions of the hydraulicsystem to be controlled and, in certain embodiments, monitored. The HTC16, as depicted, may also be located on any surface of the vehicle 10,though it may be desirable to place the HTC 16 in a location thatenables easy adjustment of hydraulic flow parameters and facileconnection/disconnection of hydraulic tools and/or hoses.

As also illustrated in FIG. 1, a remote control panel or device 52 mayalso be provided that may communicate with the control panel 50, withthe HTC 16, and/or directly with the service pack 12 via cabling orwirelessly. In a manner similar to conventional controls, then, theoperator may control or activate hydraulic, compressor, and/or generatoroutput without directly accessing either the components within theservice pack enclosure or the control panel 50. Additionally oralternatively, as described below, certain of the hydraulic tools may beintegrated with a user interface that allows specific control over theoperation of the HTC 16.

As noted above, any desired location may be selected as a convenientaccess point for one or more of the systems of the service pack 12. Inthe illustrated embodiment, for example, one or more alternating currentelectrical outputs, which may take the form of electrical receptacles 54(for AC power) and 56 (for 12 volt DC power) are provided at the panel50. Similarly, one or more pneumatic connections, typically in the formof a quick disconnect fitting, may be provided.

In the embodiment illustrated in FIG. 1, electrical applications may becoupled to the service pack 12 by interfacing with the outputs providedby receptacle 54. For example, a portable welder 58 may be coupled tothe AC electrical output 54, and may provide constant current orconstant voltage-regulated power suitable for a welding application.Similarly, DC loads may be coupled to the DC receptacle 56. Such loadsmay include lights 60, or any other loads that would otherwise bepowered by operation of the main vehicle engine 20. As mentioned above,the 12 volt DC output of the service pack 12 also serves to maintain thecharge of the vehicle battery 30, and to power any ancillary loads thatthe operator may need during work (e.g., cab lights, the HTC 16, controlsystem and load monitors, etc.).

The hydraulic applications, as noted above, are coupled to the HTC 16 asillustrated in FIG. 1. For example, a hydraulic load, illustrated as ahandheld hydraulic drill 62, may be coupled to the HTC 16 by appropriatehoses or conduits 64, 66. For example, one of the hoses 64 may provide afeed of hydraulic fluid while the other hose 66 may return the hydraulicfluid to the HTC 16 from the hydraulic drill 62. Additionally, certainof the hydraulic applications illustrated diagrammatically in FIG. 1 maybe incorporated into the work vehicle 10 and coupled to the HTC 16. Forexample, the illustrated work vehicle 10 includes a hydraulic lift,illustrated as a crane 68, which can be coupled to the HTC 16 and drivenseparately from the main vehicle engine 20. The crane 68 may include avariety of control features that enable the crane 68 to be moved in avariety of directions, illustrated diagrammatically as arrows 70, 72,74. In certain operational modes, the HTC 16 is configured such that thecrane 68 and the hydraulic drill 62 may be operated simultaneously.Additionally or alternatively, the HTC 16 is configured to selectivelyadjust the amount of hydraulic power provided to each based on feedbackindicative of a load.

In addition to providing receptacles 76 for connecting to varioushydraulic tools, the HTC 16 also includes one or more user-accessibleadjustment features 78 for switching between various operational modesof the HTC 16, for example to allow the simultaneous use of multiplehydraulic tools. As an example, the adjustment features 78 may be pushbuttons, dials, switches, a keypad, a touch screen, or any similarelectronic-based user interface. The HTC 16 may also include auser-perceivable indicator 80 for indicating the mode of operation ofthe HTC 16, such as substantially real-time hydraulic flow rates,activated tools, or the like. The user-perceivable indicator 80 mayinclude a visual indication such as a light emitting diode (LED)readout, a series of LED lights proximate one or more text or symbolicindicia, a display, an liquid crystal display (LCD) screen, a touchscreen, or a meter, among others. In certain embodiments, theuser-perceivable indicator 80 may also provide auditory alerts to theuser via one or more speakers. As an example, the auditory alerts maysound in conjunction with mode switching (automatic or manual modeswitches), errors, power on, power off, or similar operationaloccurrences. Such auditory alerts may be desirable in situations wherethe operational mode of the HTC 16 is switched automatically, or via auser interface 82 on the hydraulic tool 62. In certain embodiments, theuser interface 82 may be a part of the HTC 16, or include similarfunctions to those of a control panel on the HTC 16. The operation ofthe HTC 16 and various user interfaces are discussed in further detailbelow.

In use, the service pack 12 may provide power for the on-siteapplications 14 substantially separately from the vehicle engine 20.That is, the service engine 36 generally may not be powered duringtransit of the vehicle 10 from one service location to another, or froma service garage or facility to a service site. Once located at theservice site, the vehicle 10 may be parked at a convenient location, andthe main engine 20 may be shut down. The service engine 36 may then bepowered to provide service from one or more of the service systems(e.g., generator 38, hydraulic pump 40, and air compressor 42) describedabove. The service pack 12 also may include clutches, or othermechanical engagement devices, for selective engagement anddisengagement of one or more of the generator 38, the hydraulic pump 40,and the air compressor 42, alone or in combination with one another.

Several different scenarios may be envisaged for driving the componentsof the service pack 12, and for integrating or separating the supportsystems of the service pack 12 from those of the vehicle power plant 18.One such approach is illustrated in FIG. 2, in which the service pack 12is independent and operates separately from the vehicle power plant 18.In the embodiment illustrated in FIG. 2, as shown diagrammatically, thesupport systems for the vehicle power plant 18 are coupled to thevehicle engine 20 in the manner set forth above. The service pack 12reproduces some or all of these support systems for operation of theservice engine 36. In the illustrated embodiment, for example, thesesupport systems include a separate fuel reservoir 90, a separate aircleaner system 92, a separate cooling system 94, a separate electricalprotection and distribution system 96, a separate lube oil system 98,where desired for the engine, and a separate exhaust system 100.

Many or all of these support systems may be provided local to theservice engine 36, that is, at the location where the service engine 36is supported on the vehicle 10. On larger work vehicles, access to thelocation of the service engine 36 and the service pack 12 in general,may be facilitated by the relatively elevated clearance of the vehicle10 over the ground. Accordingly, components such as the fuel reservoir,air cleaner, cooling system radiator, electrical fuse box, and so forthmay be conveniently positioned so that these components can be readilyserviced. Also, in the illustrated embodiment, the hydraulic pump 40 andair compressor 42 are illustrated as being driven by a shaft extendingfrom the generator 38, such as by one or more belts, chains, or otherfeatures for power transmission 102. As noted above, one or both ofthese components, or the generator 38 may be provided with a clutch orother mechanical disconnect to allow them to idle while other systems ofthe service pack are operative.

FIG. 3 represents an embodiment of a configuration in which the servicepack support systems are highly integrated with those of the mainvehicle power plant 18. In the illustration of FIG. 3, for example, allof the systems described above may be at least partially integrated withthose of the vehicle power plant 18. Thus, coolant lines 110 of theservice engine 36 are routed to and from the vehicle cooling system 26,while an air supply conduit 112 of the service engine 36 is routed fromthe air intake or cleaner 24 of the vehicle engine 20. Similarly, anexhaust conduit 114 routes exhaust from the service engine 36 to theexhaust system 34 of the vehicle engine 20. The embodiment of FIG. 3also illustrates integration of the electrical systems of the vehicle 10and the service pack 12, as indicated generally by the electricalcabling 116, which routes electrical power of the service engine 32 tothe distribution system 28 of the vehicle. The systems may alsointegrate lube oil functions, such that lubricating oil may be extractedfrom both crank cases in common, to be cleaned and cooled, as indicatedby conduit 118. Finally, a fuel conduit 120 may draw fuel from the mainreservoir 22 of the vehicle, or from multiple reservoirs where suchmultiple reservoirs are present on the vehicle.

In some embodiments, integrated systems of particular interest includeelectrical and fuel systems. For example, while the generator 38 of theservice pack 12 may provide 110 volt AC power for certain applications,its ability to provide 12 volt DC output is particularly attractive tosupplement the charge on the vehicle batteries, for charging otherbatteries, and so forth. The provision of both power types, however,makes the system even more versatile, enabling 110 volt AC loads to bepowered (e.g., for tools, welders, etc.) as well as 12 volt DC loads(e.g., external battery chargers, portable or cab-mounted heaters or airconditioners, etc.).

In certain embodiments, a system may include an integration solutionbetween those shown in FIG. 2 and FIG. 3. For example, some of thesupport systems may be best separated in the vehicle 10 both forfunctional and mechanical or flow reasons. The disclosed embodimentsthus contemplate various solutions between those shown in FIG. 2 andFIG. 3, as well as some degree of elimination of redundancy betweenthese systems. In a presently contemplated embodiment, at least some ofthe support systems for the primary vehicle engine 20 are used tosupport the service pack 12 power plant. For example, at least the fuelsupply and electrical systems can be at least partially integrated toreduce the redundancy of these systems. The electrical system may thusprovide certain support functions when the vehicle engine is turned off,removing dependency from the electrical system, or charging the vehiclebatteries 30. Similarly, heating, ventilating and air conditioningsystems may be supported by the service pack engine 36, such as toprovide heating of the vehicle cab when the primary engine 20 is turnedoff. Thus, more or less integration and removal of redundancy ispossible. In this way, it should be noted that the hydraulic toolcontrol embodiments described herein may be at least partiallyintegrated with the vehicle. For example, hydraulic output control maybe done through monitoring a hydraulic load signal, or as a directcommunication of the hydraulic load through a controller area network(CAN) bus within the vehicle. As such, the methods of output control asdescribed herein may also include varying the vehicle engine 20 inaddition to or in lieu of the service engine 36. For example, inembodiments where many hydraulic loads are being applied to the serviceengine 36, the HTC 16 or a similar control feature may allow the vehicleengine 20 to provide additional power to avoid or at least mitigate thepossibility of engine overload.

The foregoing service pack systems may also be integrated in anysuitable manner for driving the service components, particularly thegenerator 38, hydraulic pump 40, and air compressor 42, and particularlyfor powering the on-board electrical system, including a control systemor similar feature. FIGS. 4A-4C illustrate diagrams of certainimplementations for driving these components from the service engine 36.In the embodiment illustrated in FIG. 4A, the generator 38 may beclose-coupled to the output of the engine 36, such as directly to theengine fly wheel or to a shaft extending from the engine 36. A sheave130 is mounted to an output shaft extending from the generator, andsimilar sheaves 132 and 134 are coupled to the hydraulic pump 40 and aircompressor 42, respectively. One or more belts 102 and/or clutches aredrivingly coupled between these components, and an idler 136 may beprovided for maintaining tension on the belt 102. Such an arrangement isshown in FIG. 4B, in which the hydraulic pump 40 is driven through aclutch 138, such as an electric clutch. It should be noted that any oneof the components may be similarly clutched to allow for separatecontrol of the components. Such control may be useful for controllingthe power draw on or the output by the engine 36, for example when noload is drawn from the particular component over a period of time, andwhen the component is not needed for support of the main vehicle enginesystems (e.g., maintaining a charge on the vehicle batteries).

These components may be supported in any suitable manner, and maytypically include some sort of rotating or adjustable mount such thatthe components may be swung into and out of tight engagement with thebelt to maintain the proper torque-carrying tension on the belt andavoid slippage. Other arrangements, such as chain drives, may also beenvisaged. In other arrangements, one or more of the components may begear driven, with gearing providing any required increase or decrease inrotational speed from the output speed of the engine 36, such as whenthe HTC 16 or other control feature adjusts the speed of the engine 36in response to an applied hydraulic load. In FIG. 4C, a support adapter140 mounts the generator 38 on the service engine 36, and the hydraulicpump 40 and air compressor 42 are driven by a gear reducer 142.

The particular component or components that are directly and/orindirectly driven by the engine 36 may be selected based upon thecomponent and engine specifications. For example, it may be desirable todirectly drive the hydraulic pump 40, and to drive the generator 38 viaa belt or gear arrangement, permitting the engine 36 to operate at ahigher speed (e.g., above 3000 RPM) while allowing a reduced speed todrive the generator or to allow a relatively low hydraulic output (e.g.,1800 RPM).

As noted above, the present disclosure is directed towards the HTC 16,which enables the simultaneous use of multiple hydraulic tools, providesan electronic interface for the user, and also adjusts hydraulic outputand/or engine speed in response to hydraulic loads. For example, the HTC16 may be a part of a hydraulic system that is connected to an engine orother prime mover for power, as discussed above. An embodiment of such ahydraulic system 150 is illustrated with respect to FIG. 5. Theillustrated hydraulic system 150 includes various features as explodedaway from one another and separate from a service vehicle. The system150 includes one embodiment of a service pack 152, which corresponds tothe service pack 12 discussed above with respect to FIGS. 1-4C. Theservice pack 152 includes at least one hydraulic pump, and isillustrated as operatively connected to one embodiment of the HTC 16,which is also connected to a heat exchanger 154, hydraulic tools, and ahydraulic fluid reservoir 156. The various connection ports of the HTC16, which provide an interface between each hydraulic line connected tothe HTC 16, are discussed below with respect to FIG. 6.

In the illustrated embodiment, the service pack 152, which includes theone or more hydraulic pumps, is configured to provide at least one flowof hydraulic fluid to the HTC 16 via a first hydraulic line 158. The HTC16, as will be discussed in further detail below with respect to FIGS.6-9, is configured to distribute the main flow of hydraulic fluid to aplurality of hydraulic tools via a plurality of hydraulic lines.Specifically, in the illustrated embodiment, the HTC 16 is configured toprovide a first flow to a hydraulic lift, such as the crane 68 of FIG.1, via an auxiliary hydraulic line 160. The HTC 16 is also configured toprovide a flow of hydraulic fluid to primary and secondary hydraulictools via primary and secondary hydraulic lines 162, 164, respectively.

Each hydraulic tool receives its respective hydraulic flow and isconfigured to use the pressurized hydraulic fluid to perform work. Thespent hydraulic fluid that results is eventually provided back to theservice pack 152 for re-pressurization. Essentially, each hydraulic toolacts as a hydraulic circuit. The spent hydraulic fluid (or unspenthydraulic fluid) that has passed through each tool circuit, duringoperation, is returned to the HTC 16. Specifically, hydraulic fluid fromthe auxiliary hydraulic tool (i.e., the hydraulic lift) is returned viaan auxiliary hydraulic return line 166. Hydraulic fluid from the primaryand secondary tools is returned via primary and secondary hydraulicreturn lines 168, 170, respectively.

The hydraulic fluid is heated as it passes from the HTC 16, through thehydraulic tools, and back to the HTC 16. Accordingly, the HTC 16 isoperatively connected to the heat exchanger 154, which is configured tocool the hydraulic fluid. Specifically, the HTC 16 is configured to flowheated hydraulic fluid through a main hydraulic exit line 172 and to theheat exchanger 154. While the heat exchanger 154 is illustrated as afan-cooled heat exchanger, other types and configurations of heatexchangers are also presently contemplated. For example, the heatexchanger 154 may include shell and tube heat exchangers, plate heatexchangers, fluid heat exchangers, or any type of heat exchanger that issuitable for cooling hydraulic fluids. After the heat exchanger 154cools the hydraulic fluid, the hydraulic fluid, during operation, flowsto the hydraulic reservoir 156 via a system return line 174.

The hydraulic fluid reservoir 156, as illustrated, is operativelyconnected to the heat exchanger 154 and the service pack 152 and isconfigured to provide a source of hydraulic fluid for use by thehydraulic pump of the service pack 152. While the hydraulic fluidreservoir 156 is illustrated as connected directly to the heat exchanger154 and the service pack 152, in other embodiments, there may beintermediate features disposed between the hydraulic fluid reservoir 156and the heat exchanger 154 and the service pack 152, such as sensors,filters, or other hydraulic fluid monitoring or conditioning features.In the illustrated embodiment, the hydraulic fluid reservoir 156receives the flow of cooled hydraulic fluid from the heat exchanger 154via system return line 174. The hydraulic fluid reservoir 156 alsoprovides a flow of hydraulic fluid, which may include at least some ofthe hydraulic fluid that is cooled at the heat exchanger 154, to theservice pack 152 via suction line 176. For example, the pump of theservice pack 152 may pull an amount of hydraulic fluid from thereservoir 156 for pressurization and provision to the HTC 16. Thehydraulic reservoir 156 is also connected to the service pack 152 via acase drain line 178, which enables the reservoir 156 to receivehydraulic fluid that may build up inside the case of the one or morepumps of the service pack 152. This drained hydraulic fluid may alsocontribute to the hydraulic fluid that is provided to the HTC 16 by theservice pack 152.

Again, the HTC 16 is configured to receive the pressurized hydraulicfluid from the service pack 152 and provide the pressurized fluid tomultiple hydraulic tools in a controlled manner. A perspective view ofan embodiment of the HTC 16 is illustrated in FIG. 6, and depicts aplurality of connection ports and control features for providinghydraulic flow to hydraulic tools and switching the hydraulic flow asdesired. The illustrated HTC 16 includes a front face 180, a back face182 configured to mount against a work vehicle or other surface, andfirst and second side faces 184, 186. The perspective view of FIG. 6provides a view of the front, back, and first side faces 180, 182, 184,while FIG. 7 provides a side view of the second side face 186.

The front face 180 of the HTC 16 includes a plurality of hydraulicconnections 188 and a plurality of control inputs 190. The plurality ofhydraulic connections 188 may include any type of male or femalehydraulic hose connectors, such as threaded connectors, push-to-connectconnectors, quick connect connectors, and so on. The hydraulicconnections 188 on the front face 180 include a primary tool outconnection 192, a primary tool return connection 194, a secondary toolout connection 196, and a secondary tool return connection 198. Theprimary tool out connection 192 is configured to connect to the primaryhydraulic line 162 of FIG. 5 and output a primary flow of pressurizedhydraulic fluid from the HTC 16 to a primary tool. The primary toolreturn connection 194 is configured to connect to the primary hydraulicreturn line 168 and receive a flow of heated and, in certainembodiments, used hydraulic fluid from the primary hydraulic tool.Similarly, the secondary tool out connection 196 is configured toconnect to the secondary hydraulic line 164 and output a secondary flowof pressurized hydraulic fluid from the HTC 16 to a secondary hydraulictool. The secondary tool return connection 198 is configured to connectto the secondary hydraulic return line 170 and receive a flow of heatedand, in certain embodiments, used hydraulic fluid from the secondaryhydraulic tool. While the illustrated embodiment depicts the HTC 16 ashaving connections for a primary and secondary tool, it should be notedthat the HTC 16 may have any number of hydraulic connections, such thatone, two, three, four or more hydraulic tools may be connected to thefront face 180 of the HTC 16. For example, the HTC 16 may include 1 to20, 2 to 10, or 3 to 5 sets of output and return connections 188 tosupport any number of hydraulic tools.

In addition to the connections 188 on the front face 180, the HTC 16also includes a main pump connection 200 and an auxiliary tool outconnection 202 on the first side face 184. The main pump connection 200is configured to connect to the first hydraulic line 158 of FIG. 5 andreceive a main flow of pressurized hydraulic fluid from the pump of theservice pack 152. Again, the HTC 16 distributes this main flow ofpressurized hydraulic fluid to multiple hydraulic tools to enablesimultaneous use of the same, such as the primary tool connected toconnections 192 and 194, the secondary tool connected to connections 196and 198, and/or an auxiliary tool connected via connection 202. In oneembodiment, the auxiliary tool out connection 202 is configured toconnect to the auxiliary hydraulic line 160 of FIG. 5, and receive aflow of heated and, in certain embodiments, used hydraulic fluid fromthe auxiliary hydraulic tool.

One such auxiliary tool, as noted above, may include a hydraulic lift(e.g., a crane, man lift, stabilizer) that may be activatedsimultaneously with at least one other hydraulic tool, such as a primaryhydraulic tool. Examples of hydraulic tools include but are not limitedto, a hydraulically driven lift, wrench, saw, clamp, drill, press,lathe, machining tool, grinder, or any combination thereof. Indeed, inaccordance with present embodiments, the HTC 16 provides a usable amountof hydraulic fluid to the hydraulic lift in most of its operationalmodes. Additionally, in situations where no other hydraulic tools areactivated other than the hydraulic lift, the HTC 16 may provide a fullhydraulic flow (i.e., up to the capabilities of the pump and otherequipment) to the hydraulic lift. For example, in an embodiment wherethe pump of the service pack 152 has the ability to output 10 GPM ofhydraulic fluid to the HTC 16, the HTC 16, in certain modes, mayprovide, approximately, the full 10 GPM flow to the hydraulic lift.Indeed, in situations where the HTC 16 is off, or in embodiments wherethe flow control is off, the HTC 16 may send full hydraulic flow to theauxiliary hydraulic tool (e.g., the hydraulic lift). Accordingly, theHTC 16 may be configured to provide a controlled amount of hydraulicpower to one, two, three, or more of a plurality of hydraulic toolsoperating alone or in combination. Various operational modes of the HTC16 are discussed in further detail below with respect to FIGS. 15-18.

As noted above, the front face 180 of the HTC 16 also has the pluralityof control inputs 190, which includes an electronic power switch 204, anelectronic tool circuit switch 206, and an electronic flow port selectswitch 208. While the control inputs 190 are illustrated as push buttonsthat interface with an electronic circuit in FIG. 6, they may beimplemented together or separately as any user interface, such as dials,keypads, touchscreens, or similar electronic adjustors. Indeed, it maybe desirable to have electronic adjustments rather than mechanicaladjustment, as mechanical adjustments may be susceptible tomisadjustment, inaccurate flows, or other user-based inaccuracies whichcan lead to time inefficiencies and, in some cases, improper tool use.

The electronic power switch 204 allows the user to turn the HTC 16 onand off, which may cut off all hydraulic flow from the HTC 16 to thehydraulic tools. For example, when the electronic power switch 204 ispushed such that the HTC 16 is off, the HTC 16 may send signals to theservice pack 152 to stop pumping hydraulic fluid. The electronic toolcircuit switch 206 enables a user to activate the flow control modesperformed by the HTC 16. For example, in situations where the electronictool circuit switch 206 is pressed such that the tool circuit control ofthe HTC 16 is off, the HTC 16 may provide full hydraulic flow to theauxiliary tool circuit, such as a crane. However, in embodiments wherethe electronic tool circuit switch 206 is pressed such that the HTC 16is performing active tool control, the HTC 16 may flow certain amountsof hydraulic fluid to each hydraulic tool depending on certain factors,such as user input, sensor feedback (e.g., load sense), active controlmode (e.g., each mode distributes hydraulic power in a differentcontrolled manner), a priority control scheme (e.g., each hydraulic toolhas a priority level for hydraulic power), the type of tool (i.e.,primary vs. secondary vs. auxiliary), the capabilities of the pump ofthe service pack 152, and/or the capabilities of the engine of theservice pack 152 and/or the work vehicle 10, among others.

To provide user input with regard to desired tool flow, the HTC 16 alsoincludes the electronic flow port select switch 208, which enables theuser to electronically adjust the output of the HTC 16 to certainhydraulic tools but not others, and also enables the user to adjust theflow rate of hydraulic fluid to the hydraulic tools. In other words, theelectronic flow port select switch 208 may essentially be a mode selectswitch that enables a user to switch between active control modes. Themodes that are selected by the user may be indicated or displayed via auser-perceivable indication, such as a visual and/or auditoryindication. While the HTC 16 may have any number of modes, flow schemes,and so forth, in the illustrated embodiment, the HTC 16 includes aplurality of LEDs 210, which may each be disposed proximate certain textor symbolic indicia corresponding to certain modes of the HTC 16. Forexample, the LEDs 210 may each be disposed proximate indications such as“5 GPM,” which indicates a certain mode corresponding to a flow rate of5 gallons per minute (GPM). In certain embodiments, such an indicationmay correlate to the flow rate provided to the primary hydraulic tool.Alternatively or additionally, certain of the indications may correlateto the flow rate and the tool, such as “5 GPM Tool A,” which indicates a5 GPM flow to the primary hydraulic tool. Further, certain indicationsmay correlate to flow rate and tool combinations, such as “5+5 GPM,”which may indicate 5 GPM to the primary tool circuit (e.g., Tool A) and5 GPM to the secondary tool circuit (e.g., Tool B). In Table 1 below,one embodiment of the modes of the HTC 16, corresponding to various flowrates to the hydraulic tools, is provided.

TABLE 1 Output Flow Rates Available Flow to Aux Available Flow to AuxEngine Mode Port A (±10%) Port B (±10%) (Tool A or B in use) (Tool A orB not in use) Speed Off 0 GPM (0 lpm) 0 GPM (0 lpm) N/A 10 GPM (37.8lpm) 1800 RPM 5 GPM 5 GPM (18.9 lpm) 0 GPM (0 lpm) 5 GPM (18.9 lpm) 6GPM (22.7 lpm) 1800 RPM 8 GPM 8 GPM (30.3 lpm) 0 GPM (0 lpm) 2 GPM (7.5lpm) 6 GPM (22.7 lpm) 2600 RPM 10 GPM 10 GPM (37.8 lpm) 0 GPM (0 lpm) 0GPM (0 lpm) 6 GPM (22.7 lpm) 3200 RPM 5 + 5 GPM 5 GPM (18.9 lpm) 5 GPM(18.9 lpm) 0 GPM (0 lpm) 0 GPM (0 lpm) 3200 RPM

In Table 1, Port A corresponds to the flow provided to the primary tool(i.e., the primary tool circuit), Port B corresponds to the flowprovided to the secondary tool (i.e., the secondary tool circuit), andAux corresponds to the flow provided to the auxiliary tool (i.e., theauxiliary tool circuit), such as a hydraulic lift. In the “Off” mode,the active flow control of the HTC 16 is off, and full hydraulic output(e.g., 10 GPM, assuming that the hydraulic output of the pump is set to10 GPM) is provided to the auxiliary tool circuit. In the “5 GPM” mode,a maximum of 5 GPM is provided to the primary tool circuit (e.g., ToolA) and no flow is provided to the secondary tool circuit (e.g., Tool B).In situations where the primary tool circuit is in use, a maximum of 5GPM is provided to the auxiliary tool circuit, and in situations wherethe primary tool circuit is not in use, a maximum of 6 GPM is providedto the auxiliary tool circuit. In other words, in such a mode, which maybe considered a first mode, when other hydraulic tools are not in use,the flow to the auxiliary tool circuit may be supplemented and 4 GPM ismaintained to the primary tool circuit. In the 8 GPM mode shown in Table1, which may be considered to be a second mode, the maximum hydraulicflow to the primary tool circuit may be 8 GPM and no flow is provided tothe secondary tool circuit. In situations where the primary tool circuitis in use, a maximum of 2 GPM is provided to the auxiliary tool circuit(i.e., the maximum capable flow of the pump less the flow to the primarycircuit), and in situations where the primary tool circuit is not inuse, a maximum of 6 GPM is provided to the auxiliary tool circuit (i.e.,4 GPM is maintained to the primary tool circuit). The 10 GPM mode, whichmay be considered a third mode, the HTC 16 is configured to output fullhydraulic flow to the primary tool circuit and no flow to otherhydraulic tools. However, when the primary tool circuit is not in use, aflow of 6 GPM is provided to the auxiliary tool circuit. Moving to theentry in Table 1 corresponding to the “5+5 GPM” mode, which may beconsidered a fourth mode, the flow to the primary and secondary toolcircuits is substantially the same, and the auxiliary tool circuitreceives no flow.

It should be noted that Table 1 is just one example of many possiblemodes of operation of the HTC 16. Indeed, the HTC 16 can have any numberof modes where the hydraulic fluid is split into multiple flows andprovided to the various hydraulic tools in certain ratios. For example,in some embodiments, the primary, secondary, and auxiliary hydraulictools may all simultaneously receive an amount of hydraulic fluiddependent on a designated priority, a load sense at each tool, theamount of flow being used by each tool, available flow, or anycombination thereof. Indeed, keeping in mind that any number of toolsmay be used, the primary, secondary, and auxiliary tools may havehydraulic flow ratios represented by A:B:C, where each of A, B, and Crange between 0 (no flow) and 100 (full flow). The flow rates of eachoutput to the tools may be independently variable, or the flows may beinterdependent. Further, the modes of the HTC 16 may be fixed ratios ofA:B:C, or the ratios of A:B:C may be adjusted. In certain embodiments,the HTC 16 may be programmable such that a user may adjust the ratiosassociated with a particular mode. Further, the HTC 16 may be coupled toand/or include features configured to learn from the use of eachhydraulic tool.

As an example of varying flow ratios, as one flow output is adjusted,such as an adjustment of the primary flow to the primary tool, the otherflows (e.g., either or both of the secondary or auxiliary flow) may alsoadjust. Further, the adjustment may be dependent on a total availableflow. For example, for a total flow of 10 GPM output by the hydraulicpower source, as the flow to the primary tool increases from 5 GPM to 6GPM, the flows to the secondary and/or auxiliary tools may be adjustedsuch that their total combined flow is reduced from 5 GPM to 4 GPM.

As noted above, it may be desirable to switch between modes. In certainsituations, it may be impractical to return to the service vehicle 10 toswitch between modes on the HTC 16. Accordingly, the HTC 16 may alsoperform load sensing that enables it to switch between modes such asthose described above automatically in response to an indication of ademand. For example, in situations where the HTC 16 is in 5+5 GPM modeand the user attempts to use the auxiliary tool circuit, the HTC 16 mayperform a routine that determines if the use of the auxiliary toolcircuit is allowable. If such use is determined to be allowable, the HTC16 may automatically change flow rates and flow ports that allow the useof the auxiliary tool circuit. Switching between modes may also beaccomplished via user input at the tool, as described in further detailbelow.

It will also be appreciated upon review of Table 1 that certain of themodes of the HTC 16 correspond to certain speeds of the engine.Specifically, in the embodiment represented by Table 1, these enginespeeds correspond to the service engine 36 of the service pack 12, 152.Indeed, as is discussed in detail below, the HTC 16 may be configured toadjust the speed of the engine 36 to provide sufficient hydraulic outputfor a given hydraulic load or mode, for example to prevent engineoverload and to supply ample power for a given task. In certainembodiments, such as when the hydraulic system is a standalone system(i.e., not part of a service pack), the HTC 16 may adjust the speed ofthe main vehicle engine 20. Such methods of operation are discussed infurther detail below.

FIG. 7 illustrates a plan view of the second side face 186 of the HTC16. The second side face 186 includes an auxiliary return connection212, a heat exchanger out connection 214, and a variety of control andmonitoring features. The auxiliary return connection 212 is configuredto connect to the auxiliary hydraulic return line 166 and receive a flowof heated and, in certain embodiments, used hydraulic fluid from theauxiliary hydraulic tool. The heat exchanger out connection 214 isconfigured to connect with the hydraulic exit line 172, which carriesheated hydraulic fluid to the heat exchanger 154 for cooling. Thecontrol and monitoring features on the second side face 186 include apressure diagnostic port 216, communications ports 218, and an accessslot 220, which enables a user to access one or more pressure adjustmentfeatures, such as a pressure relief valve 222.

The pressure diagnostic port 216 generally includes a plug positionedover an opening to the HTC 16. Once the plug is removed, a pressuregauge may be installed to the port 216, which allows a user to monitorthe pressure within the HTC 16, which may correspond to a desired flowrate. For example, in one embodiment, the user may adjust theoperational mode of the HTC 16 to a given flow rate, such as 5 GPM. Theuser may then monitor the pressure in the HTC 16 to determine whetherthe internal pressure of the HTC 16 is within an expected range for thegiven flow rate. For the 5 GPM flow rate, for example, the expectedpressure may be approximately 2200 pounds per square inch (psi)±25 psi.If the measured pressure is not within the expected range, the user maymake adjustments using the pressure relief valve 222. For example, theuser may manually adjust the internal pressure of the HTC 16 by turningthe pressure relief valve 222 with a wrench. This enables the user toadjust the internal pressure within the HTC 16 to ensure stableoperation.

The communications ports 218 include first and second communicationsports 224, 226, which enable communication between the HTC 16 andvarious devices, such as the service pack 12, 152, remote panels,control panels, diagnostic tools, controllers, computing devices, and soon. While the first and second communications ports 224, 226 areillustrated as Ethernet connections, it should be noted that anycommunications interface may be utilized that is capable of transferringcontrol and diagnostics information at a desired rate, such as universalserial bus (USB) connections, serial connections, or a combination. Inthe illustrated embodiment, the first communications port 224 isconfigured to interface with a remote panel of a service pack 12, 152,and the second communications port 226 is configured to connect with acontrol interface of the service pack 12, 152. Thus, in the illustratedembodiment, the first and second communications ports 224, 226 mayenable the HTC 16 to interface with and control certain operationalparameters of the service pack 12, 152, such as the speed of the serviceengine 36. In other embodiments, such as when the hydraulic power systemis not a part of a service pack, the communications ports 218 mayinterface directly with the vehicle 10 or other power source having anelectronic interface. In such embodiments, the HTC 16 may have theability to change the speed of the prime mover, such as the main vehicleengine 20 of FIG. 1.

As noted above, the HTC 16 in accordance with certain embodimentsenables the simultaneous use of multiple hydraulic tools in a hydraulicsystem. Additionally, in certain embodiments, the HTC 16 may adjust thespeed of a prime mover (e.g., engine 36) that drives a hydraulic powersource in response to an applied hydraulic load. Further, depending onthe nature of the applied hydraulic load, the HTC 16 may automaticallydivert a flow of hydraulic fluid to certain hydraulic tool circuits butnot others to enable the use of select hydraulic tools. FIG. 8 is ablock diagram depicting an embodiment of a hydraulic system 230including a prime mover 232, a hydraulic power source 234 driven by theprime mover 232, and an embodiment of the HTC 16 configured to controland monitor the flow of hydraulic fluid from the hydraulic power source234 to a primary tool 236, a secondary tool 238, and an auxiliary tool240 (e.g., a hydraulic lift).

The prime mover 232 that drives the hydraulic power source 234 may be aservice engine of a service pack, an engine of a standalone hydraulicsystem, or a main vehicle engine of a service vehicle that is integratedwith certain hydraulic features, as discussed above. In certainembodiments, the prime mover 232 may have multiple speeds, such as atleast two speeds, at least three speeds, at least four speeds, and soon. In one embodiment, the prime mover 232 may have a continuouslyvariable speed between a low and a high speed. The speed of the primemover 232 may directly affect the amount of hydraulic fluid that thehydraulic power source 234 is able to pump in a given amount of time. Inthis way, the prime mover 232 can control the flow rate of hydraulicfluid provided to the HTC 16 and, therefore, the tools 236, 238, 240.

Each hydraulic tool 236, 238, 240 forms a closed hydraulic circuit withthe hydraulic power source 234. For example, as depicted, spenthydraulic fluid that circulates through each of the hydraulic tools 236,238, 240 is eventually cycled back to a hydraulic reservoir 242. Thehydraulic power source 234 draws hydraulic fluid from the hydraulicreservoir 242 to power one or more of the hydraulic tools 236, 238, 240.The HTC 16, in the illustrated embodiment, includes or is otherwiseoperatively connected to a pressure switch 244 that is able to monitorthe flow of hydraulic fluid from the hydraulic tools 236, 238, 240. Forexample, in the illustrated embodiment, the HTC 16 includes a pressuremonitor 246, which monitors the flow from at least the primary tool 236and the secondary tool 238 and sends the flow with the higher flow rateor pressure to the pressure switch 244. The pressure switch 244 may actas a thresholding device, and, when a flow rate or pressure indicativeof an applied hydraulic load is passed to the pressure switch 244, thepressure switch 244 may be triggered. For example, the pressure switch244 may be set to a certain pressure or flow rate. When the pressuremonitor 246 sends a flow having a flow rate or a pressure higher thanthe setting of the pressure switch 244, the pressure switch 244 istriggered.

When the pressure switch 244 is triggered, one or more signals may beprovided to a control circuit 248 that are indicative of the pressure orflow rate, which indicates a demand for hydraulic power. The controlcircuit 248, in response, is configured to adjust the speed of the primemover 232. Further, in certain embodiments, the speed to which the primemover 232 is adjusted by the control circuit 248 may be a function ofthe applied hydraulic load. For example, the control circuit 248 maycontinuously vary the speed of the prime mover 232 over a speed rangebased on the applied hydraulic load (or demand), or may increase ordecrease the speed of the prime mover 232 by a series of discrete speedsteps, as shown in Table 1 above, where the load applied (or the demand)may correlate with a certain optimal speed or speed range of the primemover 232. Thus, the control circuit 248 may continuously vary or varyin a stepwise fashion the speed of the prime mover 232 based on acertain relationship between the applied load or the applied demand andthe speed of the prime mover 232. For example, the control circuit 248may vary the speed of the prime mover 232 based on a load matchingrelationship, based on a series of load thresholds (where each loadthreshold corresponds to a different prime mover speed), a proportionalrelationship with the applied load, or any other relationship (e.g., afunction, a curve, a graph, a matrix, an equation) that varies(continuously or in a stepwise fashion) the speed of the prime mover 232based on the load. Generally, the control circuit 248 varies the speedof the prime mover 232 over a plurality of speeds between an “off” stateand a maximum speed or between an idle speed and the maximum speed. Inthis way, the speed of the prime mover 232 may have more speeds than maybe correlated to only “on” and “off” states or idle and max states. Amethod corresponding to the control of prime mover speed based onapplied load is discussed in further detail below with respect to FIG.11.

Alternatively or additionally, the HTC 16 includes a plurality of flowcontrol devices that are configured to provide select hydraulic flows tothe hydraulic tools 236, 238, 240 based on user input and, in certainembodiments, sensed load demand. In the illustrated embodiment, forexample, the HTC 16 includes a flow regulator 250, which is configuredto receive a pressurized flow of hydraulic fluid 251. The flow regulator250 may include one or more valves for splitting the pressurized flow251 into a primary flow 252 provided to the primary tool 236 and asecondary flow 254 provided to a flow diverter 256. The flow regulator250 is also configured to adjust the amount of hydraulic fluid, and thusthe flow rates and pressure of the hydraulic fluid, for each of theprimary and secondary flows 252, 254 using the one or more valves.Indeed, the flow regulator 250 may split the primary and secondary flows252, 254 over any flow ratio. For example, the flow regulator 250 maysplit the pressurized flow 251 into a primary:secondary flow ratio of0:1, 1:0, 1:1, 2:1, 1:2, and so on. Further, the flow ratio for theprimary flow 252 and the secondary flow 254 may be represented by X:Y,where X and Y each range between 0 and 100.

The valves contained in the flow regulator 250 may be manually orelectronically operated. However, in certain embodiments, electronicallyactivated valves may be desirable to interact with the HTC 16. Forexample, in embodiments where the flow regulator 250 includes one ormore solenoid valves, the valves may be displaced using electricalsignals, which reduces the potential for operator error and canfacilitate automatic or semi-automatic control of the primary andsecondary flows 252, 254 using one or more control circuits, asdescribed below. Indeed, in one embodiment, as the user makes electronicadjustments to the operational modes of the HTC 16 (e.g., via pushbutton entries), the one or more valves of the flow regulator 250 mayadjust their relative displacements to cause different flow rates tooccur for the primary and secondary flows 252, 254. Further, in someembodiments, the control circuit 248 and/or the HTC 16 may monitor theone or more valves of the flow regulator 250 to stabilize flow rates.For example, the valves of the flow regulator 250 may be monitored forfeedback indicative of a difference between a monitored flow rate versusa target flow rate for each of the primary and secondary flows 252, 254.The HTC 16 and/or control circuit 248 may automatically adjust thepositions of the valves in response to this monitoring for flow ratestabilization.

In embodiments where the valves of the flow regulator 250 areelectronically adjustable (e.g., via an electronic control signal), thecontrol circuit 248 and/or the HTC 16 may be configured to calibrate theelectronic signals provided to the valves versus their position. In thisway, a certain electrical signal may be correlated to a certain valveposition. In some embodiments, the HTC 16 and/or the control circuit 248may also calibrate the electronic input to the one or more valves of theflow regulator 250 at least partially based on at least one property ofthe hydraulic fluid, such as density, viscosity, boiling point, or otherfluid parameters.

As noted above, the primary flow 252 is provided to the primaryhydraulic tool 236 for use in a given application, while the secondaryflow 254 is provided to the flow diverter 256. The flow diverter 256also includes one or more valves and is configured to provide thesecondary flow 254 to the secondary tool 238 and/or the auxiliary tool240, which in the illustrated embodiment is a hydraulic lift. Whetherthe secondary flow 254 is provided to either of the secondary tool 238or the auxiliary tool 240 may depend on user input, sensed load demand,or both. Additionally or alternatively, the secondary flow may be splitbetween the secondary tool 238 and the auxiliary tool 240 in any ratio,such as 0:1, 1:0, 1:1, 2:1, 1:2, and so on, based at least on the userinput, sensed load demand, or both. Further, the flow rate split may berepresented by Y:Z, where Y and Z both range between 0 and 100. Forexample, the flow diverter 256 may be movable between a first position,where the secondary flow 254 is directed to the secondary tool 238, anda second position, where the secondary flow 254 is directed to theauxiliary tool 240. In such embodiments, when the flow diverter 254 isenergized, the flow diverter 254 is in the first position (i.e., no flowto the auxiliary tool 240), and when the flow diverter 254 is notenergized, it is in the second position (i.e., no flow to the secondarytool 238). In certain of these embodiments, depending on the electricalinput provided to the flow diverter 256, the flow diverter 256 may becontinuously varied between its first and second positions. Indeed, theHTC 16 and/or the control circuit 248 may be configured to calibrate theelectrical input to the flow diverter 256 in a similar manner to thosedescribed above for the flow regulator 250 (e.g., based on monitoredversus target flow rates, valve positions, and/or hydraulic fluidproperties).

A user may select a certain operational mode corresponding to the use ofonly the primary and secondary tools 236, 238. In such a mode, thesecondary flow 254 is provided to the secondary tool 238, rather thanthe hydraulic lift 240, which prevents the use of the hydraulic lift240. However, in embodiments where the user selects an operational modethat corresponds to the activation of the primary tool 236 only, or theprimary tool 236 and the hydraulic lift 240, the secondary flow 254 isprovided to the hydraulic lift 240. It should be noted that in certainembodiments, such as when full hydraulic flow is provided to the primarytool 236 during use, the hydraulic lift 240 may not be able to be used,as no excess flow is available. However, when the primary tool 236 isnot being used in such a mode, the hydraulic lift 240 may receive ausable flow of hydraulic fluid via the secondary flow 254. That is, aflow rate of hydraulic fluid provided to the hydraulic lift 240 may bemaintained above a minimum level. The minimum level may correspond tothe lowest flow rate possible to maintain full or near-full operationalcapability of the hydraulic lift 240. Moreover, in embodiments where anoperational mode other than full flow to the primary tool 236 isselected, a usable amount of hydraulic fluid may be provided to thehydraulic lift 240, even when the primary tool 236 is in use. Again,while the user may make adjustments and change between such operationalmodes, the HTC 16 may automatically switch between the modes based on asensed load demand by an inactive tool (i.e., a tool to which no flow isprovided), or an increased demand by an active tool. The modes also mayauto switch based on a priority control scheme, which may be pre-definedor user-programmable via the HTC 16.

Indeed, the HTC 16 may be configured to adjust certain operationalparameters, such as flow rates, engine speeds, split of hydraulic flows,and so on, based on a priority control scheme. The priority controlscheme may enable the control of hydraulic power provided to thehydraulic tools based on priority levels assigned to each tool. As anexample, the hydraulic tool that is assigned the highest priority levelmay receive hydraulic power as needed, no matter which operational modethe HTC 16 is in, and the hydraulic tool with the lowest priority may nolonger receive hydraulic power. In certain embodiments, auser-perceivable warning may be provided on the tool or on the HTC 16that the tool is about to become inactive. Such a priority scheme may beenabled using automatic hydraulic output switching systems as describedherein. Control methods relating to automatic switching of hydraulicoutput by the HTC 16 are discussed in further detail below with respectto FIGS. 12-14.

In certain embodiments, as illustrated, one or more of the hydraulictools may include a separate tool control/user interface. Further, incertain of these embodiments, the tool control/user interfaces may eachinclude a separate load sense device. Specifically, in the illustratedembodiment, the primary tool 236 includes a respective tool control/userinterface 258 with a load sense 260, the secondary tool 238 includes arespective tool control/user interface 262 with a load sense 264, andthe hydraulic lift 240 includes a lift control/user interface 266 with aload sense 268. Each user interface 258, 262, 266 may enable the user toselect certain operational modes of the HTC 16, make adjustments to flowrates provided to each tool, perform flow monitoring, and so forth.Indeed, each user interface 258, 262, 266 enable remote control of modesdirectly at their respective tools, e.g., on demand hydraulic power.Further, inputs at the user interfaces 258, 262, 266 may temporarilyoverride a mode, or auto switch modes to provide a suitable amount ofpower at the tool that the user desires to use. Embodiments of such userinterfaces are discussed below with respect to FIG. 19.

The load senses 260, 264, 268 may each be directly attached to theirrespective tool, or may each be a part of the tool control/userinterface for each as depicted. The load senses 260, 264, 268 may be atransducer or similar sensing feature that is capable of measuring anindication of load demand or of active use. For example, the load senses260, 264, 268, which may be the same or different, may include apotentiometer that measures trigger pull, a flow meter that measuresflow through the tool, a button placed on the tool control at a locationthat is unique to active use of the tool (e.g., on a trigger, on atrigger handle), or any other such indicator of use. Further, becausethe HTC 16, in certain embodiments, connects with the service pack 12,152, the load senses 260, 264, 268 may each be independently connectedto the HTC 16, the service pack 12, 152, to a remote panel of theservice pack 12, 152, or a combination.

The load senses 260, 264, 268, in some embodiments, each provide signalsto the HTC 16 indicative of a demand for hydraulic power (i.e., a flowof hydraulic fluid). The signal may be indicative of the level ofdemand, and the HTC 16 may make adjustments accordingly. For example,the HTC 16 may be in a first mode having a first flow rate of theprimary flow 252 to the primary tool 236. If the user activates theprimary tool 236 to a point where the primary tool 236 requires morehydraulic flow than the first flow rate, the HTC 16 may switch to asecond mode having a second flow rate of the primary flow 252 to theprimary tool 236, the second flow rate being higher than the first flowrate. Referring to the illustrated embodiment, the HTC 16 may cause theone or more valves of the flow regulator 250 to open by an additionalamount, enabling a higher flow of hydraulic fluid. Indeed, the amount bywhich the flow rate of the primary flow 252 increases between the firstflow rate to the second flow rate may be a function of the signalprovided to the HTC 16 by the load sense 260. That is, the amount bywhich the valves of the flow regulator 250 displace may be a function ofthe same. Similar operations may occur with the secondary tool 238 andthe hydraulic lift 240, with the flow regulator 254 choking the primaryflow 252 and increasing the secondary flow 254.

In another example, the HTC 16 may be in a first mode where the primarytool 236 and the secondary tool 238 are able to be used. In this mode,the HTC 16 does not direct hydraulic flow to the hydraulic lift 240,preventing the user from operating the hydraulic lift 240. In asituation where the user attempts to use the hydraulic lift 240, theload sense 268 of the hydraulic lift may send signals indicative of ademand for hydraulic power to the HTC 16. In certain embodiments, suchas when the secondary tool 238 is not in use, the HTC 16 may switchoperational modes, and the flow diverter 256 may send the secondaryhydraulic flow 254 to the hydraulic lift 240 rather than the secondarytool 238. Indeed, the HTC 16 may switch between many different flowrates, flow outputs, and so forth depending on the signals received fromthe load senses 260, 264, 268.

In addition to including the features described above for flow controland monitoring, the HTC 16 includes an overload protection device 270and a pressure release orifice 272. The overload protection device 270is configured to protect the primary and secondary tools 236, 238 fromdamage in situations where the pressure of the hydraulic fluid reachesor exceeds a threshold. Accordingly, the overload protection device 270may include one or more adjustable relief valves that may be adjustedbased on the specifications of the tools being used. The pressuresetting of the overload protection device 270 may be adjusted manually,i.e., using a handheld wrench or similar tool, or may be electronicallyadjusted. As an example, the overload protection device 270 may be therelief valve 222 of FIG. 7.

The pressure release orifice 272 may be a bleed down orifice of the HTC16 that releases pressure that would otherwise be trapped within the HTC16. For example, if a hydraulic tool is separated from the HTC 16, theconnection at which the tool was connected may remain pressurized. Bybleeding out hydraulic fluid (e.g., back to hydraulic fluid reservoir156 of FIG. 5), the pressure is reduced, allowing a different tool orthe same tool to be reconnected to the HTC 16. As illustrated, theoverload protection device 270 and the pressure release orifice 272 areboth generally disposed along a line 274 carrying the used hydraulicfluid from the hydraulic tools 236, 238, 240 to a heat exchanger 276. Asan example, the line 274 may be the hydraulic exit line 172 of FIG. 5.

FIG. 9 is a circuit diagram depicting one embodiment of a hydraulicsystem 290 that is configured to enable the simultaneous use of multiplehydraulic tools, automatic switching of hydraulic output, and automaticload sensing and power compensation. The system 290 includes a hydraulicpower supply 292, which is an open-center hydraulic power source that isa part of the service pack 152 of FIG. 5. The hydraulic power supply 292includes a pump 294 and a two-way solenoid proportional valve 296. Thepump 294 includes a flow compensator valve 298 and a maximum pressurecompensator valve 300, which are both pilot-operated. The flowcompensator valve 298 and the maximum pressure compensator valve 300 aregenerally configured to minimize the influence of pressure variations onthe flow output by the pump 294. The pump 294 also includes a controlpiston 302 for a variable displacement pump portion 304. The hydraulicfluid that is pumped by the pump portion 304 flows through a first pumpline 306 and through the two-way solenoid proportional valve 296. Thetwo-way solenoid proportional valve 296 is configured to adjust theamount of hydraulic fluid delivered to the HTC 16 via a main hydraulicoutput line 308. The main hydraulic output line 308 may correspond tothe first hydraulic line 158 of FIG. 5.

The hydraulic flow from the main hydraulic output line 308 reaches apressure-compensated flow regulator 310, which includes a solenoidproportional valve 312 and a four-way valve 314. As illustrated, themain hydraulic output line 308 diverges into a primary flow line 316 andan excess flow line 318. The primary flow line 316 leads to the solenoidproportional valve 312, which controls the flow rate of the primary flowto a first tool circuit 320 and thus the split between the primary flowline 316 and the excess flow line 318. As noted above with respect tothe flow regulator 250 of FIG. 8, the solenoid proportional valve 312may split the flow between the primary flow line 316 and the excess flowline 318 in a ratio represented by X:Y, where X and Y each range between0 to 100. For example, the solenoid proportional valve 312 is configuredto be electronically adjusted such that its orifice size changes inproportion to an applied electrical signal to its solenoid coil. Asnoted above, the flow rate of the primary flow may be dependent upon theoperational mode of the HTC 16, the output of the pump 294, and sensedload demands, to name a few.

The excess flow line 318 leads to the four-way valve 314, which isconfigured to open or close the excess flow provided to a secondhydraulic tool circuit 322 and/or an auxiliary hydraulic tool circuit324. In particular, the excess flow line 318 leads to a directionalcontrol valve 326, which is configured to determine how the excess flowis used, i.e., whether the excess flow is provided to the secondhydraulic tool circuit 322 and/or the auxiliary tool circuit 324. Inother words, the valve 326 controls the split of excess flow betweencircuits 322 and 324. For example, the excess flow may be provided tothe second hydraulic tool circuit 322 and the auxiliary tool circuit 324over a variable range, such as a range represented by X:Y, where X and Yrange between 0 and 100. In embodiments where the directional controlvalve 326 is fully energized, it directs the excess flow to the secondhydraulic tool circuit 322 through a secondary flow line 328. Inembodiments where the directional control valve 326 is not energized,the excess flow is directed down an auxiliary flow line 329 to theauxiliary hydraulic tool circuit 324. In addition to leading to thesecond hydraulic tool circuit 322, the secondary flow line 328interfaces with a first check valve 330. Similarly, the primary flowline 316 interfaces with a second check valve 332.

The first and second check valves 330, 332 automatically open ifpressures in the excess and primary hydraulic flows respectively exceeda pressure threshold. As illustrated, the first and second check valves330, 332 are configured such that the flow having the higher pressure(i.e., the higher of the primary or excess flow), depending on usage,flows to a pressure switch 334. The pressure switch 334 is configuredsuch that if the higher pressure flow is at or above a thresholdpressure set at the pressure switch 334, the pressure switch 334 sendsone or more signals to the HTC 16 and/or a separate controller toindicate tool use. As noted above, such an indication may result inhydraulic output switching (e.g., switching the directional controlvalve 326, the solenoid proportional valve 312, or the two-way valve314, or a combination), or increasing the output of the pump 294 byincreasing engine speed (i.e., the engine 36 of the service pack 12,152) and/or directly increasing pump output by adjusting the solenoidproportional valve 296 and/or the pump portion 304, or any combinationthereof.

After hydraulic fluid is used by the hydraulic tools, such as the firsthydraulic tool circuit 320 (e.g., a motor-driven hydraulic too)l, thesecond hydraulic tool circuit 322 (e.g., a cylinder-driven hydraulictool), and/or the auxiliary hydraulic tool circuit 324 (e.g., ahydraulic crane), then the spent hydraulic fuel is returned viarespective hydraulic return lines 336, 338, 340 to the HTC 16.Specifically, the hydraulic return lines 336, 338, 340 all lead to amain return line 342, which may correspond to the main hydraulic exitline 172 of FIG. 5. The main return line 342 is configured to carryspent hydraulic fluid from the HTC 16 to a heat exchanger 344. Asgenerally discussed above, after cooling, the hydraulic fluid isprovided to a hydraulic fluid reservoir 346.

The main return line 342, in addition to carrying the spent hydraulicfluid from the HTC 16 to the heat exchanger 344, also interfaces with arelief valve 348 and an adjustable orifice 350. The relief valve 348,which may be manually or electronically adjustable, is configured toopen based on an adjustable pressure threshold to avoid overpressurization of the HTC 16 and/or the hydraulic tools 320, 322. Theadjustable orifice 350 is configured to release any pressure (e.g.,release air) that may be otherwise trapped within the HTC 16, such aswhen a powered tool is inadvertently or purposefully detached. Thisallows hydraulic tools to be attached and detached from the HTC 16without manually releasing trapped pressure.

While the embodiment illustrated in FIG. 9 depicts the HTC 16 andhydraulic tools 320, 322, 324 as being operatively connected to ahydraulic pump of a service pack, as noted above, the presentembodiments are also applicable to any hydraulic power source, such as afixed displacement pump. FIG. 10 is a circuit diagram of an embodimentof a hydraulic system 360 where the HTC 16 receives pressurizedhydraulic fluid from a fixed displacement pump 362. It should be notedthat many of the features illustrated in FIG. 10 are the same as thecorresponding features illustrated in FIG. 9. Accordingly, thosefeatures are referenced using the same numerals. The fixed displacementpump 362, as illustrated, includes a fixed displacement pump portion 364and a pressure relief valve 366, which is connected to a return line 368leading from the HTC 16 to the heat exchanger 344. In certainembodiments, the pressure relief valve 366 may be set to a certainpressure based on the desired output of the fixed displacement pump 362.Indeed, the pressure threshold of the pressure relief valve 366 may beadjusted by the HTC 16 or another controller in response to a signalindicative of a hydraulic load or a demand for hydraulic fluid. Forexample, the pressure threshold of the pressure relief valve 366 may beincreased if a higher pressure/flow rate of hydraulic fluid is desiredfrom the fixed displacement pump 362. The operation of the hydraulicsystem 360 is generally as described above. Thus, the system 360 isconfigured to enable the simultaneous use of multiple hydraulic tools,output switching, load sensing and power compensation, or anycombination thereof.

The present embodiments, as generally discussed above, are applicable toa controller in operative connection with any hydraulic power source.Indeed, the present embodiments provide certain control/operationalmethods that may be used in conjunction with any or a combination of thesystems described herein. For example, the methods described below withrespect to FIGS. 11-14 may be stored as routines on a non-transitory,tangible, machine-readable medium that is capable of being accessed by aprocessor-based computer or controller. Additionally or alternatively,certain of the steps described herein may be performed by the HTC 16(e.g., a valve of the HTC 16) or a sensing feature in communicationwith, contained within, or otherwise operatively connected to the HTC16, such as a pressure switch, load sense line, user interface, and soon. FIG. 11 is a process flow diagram illustrating an embodiment of amethod 380 of compensating the power output by an engine in operativeconnection with a hydraulic power source in response to appliedhydraulic load. In the illustrated embodiment, the method 380 beginswith receiving a user-selected input of a desired flow rate for ahydraulic power source (block 382). As an example, the user-selectedinput may include an operational mode selection performed on the HTC 16.The selection of the desired flow rate, which may be considered a firstflow rate, may then be correlated to an initial prime mover output. Theoperational mode flow rate/tool combinations and associated enginespeeds set forth above in Table 1 may be one example.

Thus, based on the user-selected input, the HTC 16 or other controllermay then set an initial prime mover (e.g., engine 36) based on theuser-selected input (block 384). This initial output may be considered afirst engine speed. Once the engine is at the first engine speed, theHTC 16 and/or associated controller and sensors monitor the pressureand/or flow rate of hydraulic fluid that is used by each hydraulic toolconnected to the HTC 16 (block 386). For example, as set forth abovewith respect to FIG. 8, the pressure monitor 246 may monitor the flowthrough the lines that are connected to any one or a combination ofhydraulic tools connected to the HTC 16. Alternatively or additionally,one or more load sensing features may be integrated with or otherwiseoperatively connected to each hydraulic tool, such that the load sensingfeatures may send indicative signals to the HTC 16 and/or controller inoperative connection with the HTC 16.

The HTC 16 and/or controller then determines if the highest of pressuresin the different hydraulic flow lines (or highest of flow rates) isabove a pressure threshold (or a flow rate threshold) (query 388). Forexample, the pressure switch/load sense 244 of FIG. 8 may be set to acertain pressure or flow rate threshold such that when triggered, asignal indicative of a load may be provided to the HTC 16 and/or thecontrol circuit 248, either or both of which may be in communicationwith the prime mover 232. In embodiments where the pressure or flow rateis not above the threshold (e.g., the pressure switch/load sense 244 isnot triggered), the method 380 cycles back to monitoring (block 386).

However, in embodiments where the pressure or flow rate is above thethreshold (e.g., the pressure switch/load sense 244 is triggered andsends a signal to the HTC 16 and/or control circuit 248), the speed ofthe prime mover is adjusted to accommodate the load demand (block 390).For example, the HTC 16 and/or the control circuit 248 may send one ormore control signals to the prime mover 232 to increase its speedaccording to the higher output demand. As noted above, the speedincrease may generally be a function of the load demand. Thus, the speedadjustment may be a load matching adjustment where the speed of theprime mover is continuously varied throughout a speed range of the primemover, a step-wise adjustment to a higher speed of the prime mover(e.g., through a plurality of speeds) that is capable of providingadequate output (e.g., through the speeds set forth in Table 1) for theload, or the adjustment may be an adjustment that is proportional orotherwise continuously variable with the increase in demand but not anactual load matching adjustment (i.e., the speed may not be exactlymatched with the load).

In addition to, or in lieu of performing the output adjustment method380 described above, the HTC 16 may also perform output switchingmethods, as described below with respect to FIGS. 12-14. FIG. 12illustrates a process flow diagram of a general method 400 forperforming hydraulic output switching in response to a user input and/oran applied load. Method 400, as illustrated, includes determiningwhether the flow control of the HTC 16 is activated (query 402). Inembodiments where the flow control has not been activated, such as whenthe valves of the HTC 16 are not being controlled and are in theirrespective non-energized positions, the full flow received by the HTC 16is provided to the auxiliary tool (block 404). As an example, when theuser has not turned on the flow regulation and flow control features ofthe HTC16, full hydraulic fluid flow may be provided to the hydrauliclift 240 of FIG. 8.

However, in embodiments where the flow control is activated, the HTC 16receives a user-selected input of a desired flow rate and toolcombination (block 406). In other words, the user selects a certainoperational mode corresponding to which tools the user desires to useand which flow rate is appropriate, or believed to be appropriate at thetime of choosing. It should be noted that the user selection may be atan interface at the HTC 16, or using a user interface that is attachedor otherwise operatively connected to a hydraulic tool in communicationwith the HTC 16. The user interface may be or include a series ofbuttons, a keypad, a touchscreen, or other feature. Embodiments of userinterfaces are described in further detail below with respect to FIG.19.

The HTC 16, depending on the user selection, determines whether thesecondary hydraulic tool has been activated (query 408). In other words,the HTC 16 determines how the excess flow is used while the primary flowis provided to the primary tool. For example, the HTC 16 may receive theuser input at block 406, and may divert a flow of hydraulic fluid to thesecondary tool 238 or to the hydraulic lift 240 of FIG. 8. Inembodiments where the user selects the use of the auxiliary tool, suchas the hydraulic lift 240, the HTC 16 sends the excess flow to theauxiliary tool and the primary flow to the primary tool, and performs aprimary/auxiliary tool flow routine (block 410), which is described infurther detail below with respect to FIG. 14. As an example, referringto FIG. 9, the directional control valve 326 may be left off, in whichcase the excess flow is sent along the auxiliary flow line 329 and tothe auxiliary hydraulic tool circuit 324. Returning to FIG. 12, inembodiments where the secondary tool is activated, the excess flow issent to the secondary tool and the primary flow is sent to the primarytool, and a primary/secondary tool flow routine is performed (bock 412),which is described in further detail below with respect to FIG. 13. Forexample, referring again to FIG. 9, the directional control valve 326may be energized and the excess flow sent along the secondary flow line328 and to the secondary hydraulic tool circuit 322.

FIG. 13 is a process flow diagram of an embodiment of aprimary/secondary flow control routine 420, which may be performed afteror in conjunction with method 400 of FIG. 12. The routine 420 startswith sending the primary flow to the primary tool circuit and the excessflow to the secondary tool circuit (block 422). As noted above, the actsrepresented by block 422 may include energizing the directional controlvalve 326 of FIG. 9. The pressure/flow rate of the hydraulic fluid tothe primary and secondary tool circuits is then monitored (block 424) asdescribed above with respect to either of FIG. 8 or 9. As the HTC 16performs this monitoring function, the HTC 16 may also determine whetherthe user has attempted to use the auxiliary tool (query 426). Forexample, the monitoring may simply include passive acts, such as waitingfor a signal indicative of a demand for hydraulic fluid, or may includemore active monitoring, such as by sending signals, substantiallycontinuously or at intervals, to the auxiliary tool to determine thepresence of an indicator of demand, such as a trigger position on anauxiliary tool control.

In embodiments where no attempt to use the auxiliary tool is made, themethod 420 continues monitoring. However, in embodiments where the userattempts to use the auxiliary tool, the HTC 16 may determine whether thesecondary tool is in use (query 428). In embodiments where the secondarytool is in use, the HTC 16 does not change output, and may also providean error indication to the user, such as a visual, auditory, and/ortactile indication to the user that the simultaneous use of thesecondary and auxiliary tool is not allowed (block 430). However, inembodiments where the secondary tool is not in use, the HTC 16 may sendthe excess flow to the auxiliary tool (e.g., by turning the directionalcontrol valve 326 of FIG. 9 off) and perform a primary/auxiliary flowroutine (block 410).

FIG. 14 is a process flow diagram of an embodiment of aprimary/auxiliary flow routine 440 that may be performed by the HTC 16.The method begins with sending the primary flow to the primary tool andsending the excess flow to the auxiliary tool, which may be a hydrauliclift, such as a crane (block 442). The HTC 16 then monitors the pressureand/or flow used by the hydraulic tools (block 444). For example, theHTC 16 may monitor the pressure and/or flow rate of the hydraulic fluidprovided to the primary tool and/or the auxiliary tool. Additionally oralternatively, any one or a combination of the hydraulic tools mayinclude a load sense that is configured to send signals to the HTC 16indicative of a demand for hydraulic fluid. In such embodiments, theload sense may monitor certain features of a tool control that indicatea demand for hydraulic fluid, such as hydraulic pressure, hydraulicfluid flow rate, a trigger position, a handle sensor, a potentiometer,or the like. As noted above with respect to FIG. 13, the monitoring thatis performed may be passive or active monitoring.

While monitoring the hydraulic demand for each tool, the HTC 16 may alsodetermine whether the primary tool is in use (query 446). In embodimentswhere the primary tool is not in use, the HTC 16 supplements the excessflow with additional hydraulic fluid that would otherwise be sent to theprimary tool (block 448). For example, if the excess flow has beenselected to have a flow rate of 5 GPM, if the primary tool is not inuse, then the excess flow may be supplemented with additional hydraulicfluid such that it has a flow rate of 6 GPM. However, any suitablecombination of flow rates may be used. The routine may then cycle backto monitoring in accordance with block 444.

In embodiments where the primary tool is in use, then the HTC 16continues monitoring pressures and/or flow rates (block 450). Whileperforming its monitoring, the HTC 16 also determines whether the userhas attempted to use the secondary hydraulic tool (query 452). As notedabove, this monitoring process may be passive or active. That is, theHTC 16 may respond to signals indicative of a demand for hydraulic fluid(e.g., by signals generated at the tool), or may actively determine thestate of each tool. In embodiments where the user has not attempted touse the secondary hydraulic tool, the routine may cycle back to themonitoring acts of block 450. However, in embodiments where the user hasattempted to use the secondary tool, the HTC 16 may determine whetherthe auxiliary hydraulic tool is in use (query 454).

In embodiments where the auxiliary tool is in use, the HTC 16 mayprovide a user-perceivable indication that the secondary tool may not beused (block 456). For example the HTC 16 may provide an auditory,visual, and/or tactile indication that the secondary tool may not beused. However, in embodiments where the auxiliary tool is not in use,the HTC 16 may send the excess flow to the secondary tool and theprimary flow to the primary tool, and may begin performing aprimary/secondary flow routine (block 412), which may be the routine 420described above. For example, referring to FIG. 9, the directionalcontrol valve 326 may be energized, sending the excess flow to thesecondary flow line 328.

As discussed above, the HTC 16 may be used in conjunction with anyhydraulic power source capable of providing a flow of hydraulic fluid ata pressure sufficient for use with hydraulic tools. The flow ofhydraulic fluid to the tools is controlled by the HTC 16, which alsoenables a user to make electronic adjustments to ratios or splits of thehydraulic power among multiple tools, flow rates, pressures, toolactivation, and so forth. Thus, in addition to providing internalcomponents that may be automatically and/or manually controlled andadjusted, the present disclosure provides example embodiments ofinterfaces for the HTC 16 as well as hydraulic tool interfaces that mayrelay information to the HTC 16.

Indeed, FIGS. 15-18 illustrate example embodiments of interfaces for theHTC 16. Furthermore, it should be noted that while these interfaces aredescribed in the context of faceplates for the HTC 16, that any or acombination of their features may be incorporated into a user interfacefor a hydraulic tool in operative connection with the HTC 16, such thatthe user interface enables similar or the same control over theoperation of the HTC 16 as the faceplates described herein.Specifically, FIG. 15 illustrates an embodiment of a faceplate 460 thatis configured to be placed against the front face 180 of the HTC 16(FIG. 6). The faceplate 460 includes a hydraulic connector section 462and a user input/indicator section 464. The hydraulic connector section462 includes hydraulic fluid supply and return connectors for both theprimary tool and the secondary tool. As illustrated, the faceplate 460includes a primary tool supply connector cover 466, and a text indicatorlabeling the connector under the connector cover 466 as “Pressure PortA.” Of course, the text indicia discussed herein may be any text orsymbolic indicia capable of communicating the functionality of thefeature corresponding to the indicia. Proximate the connector cover 466,a primary tool return connector cover 468 corresponding to the connectorfor the hydraulic return line from the primary tool is provided. A textindicator is also provided proximate labeling the primary tool returnconnector cover 468 as “Return Port A.” In the illustrated embodiment,the connector cover 468 is below the connector cover 466. However, itshould be noted that the interfaces and faceplates described herein mayhave any arrangement corresponding to the particular connector placementon a given hydraulic tool control. The faceplate 460 further includes asecondary tool supply connector cover 470 and a secondary tool returnconnector cover 472. Connector cover 470 is labeled as “Pressure PortB,” and connector cover 472 is labeled as “Return Port B.” Because theHTC 16 may include any number of pressure and return connections, thefaceplate 460 may include any number of pressure and return port sets,such as 1 to 20, 2 to 10, or 3 to 5 sets.

The faceplate 460 may also include various instructions, warnings, orother text or symbolic indicia, which are provided to facilitate the useof the HTC 16. In the illustrated embodiment, a series of symbolicwarnings 474 are provided, along with text 476 indicating the nature ofthe controller attached to the faceplate 460. The faceplate 460 alsoincludes an area 478 for any other indicia, such as brand names,personalization, or the like.

The user input/indicator section 464 of FIG. 15 includes a plurality ofbuttons configured to enable the user to electronically switch betweenvarious operational modes of the HTC 16, such as modes where the HTC 16enables the simultaneous use of multiple hydraulic tools. The buttonsincludes a power on/off button 480, which enables the user to turn theHTC 16 on and off. An indicator 482, which in the illustrated embodimentincludes an LED light 482, is provided proximate the power on/off button480 to indicate to the user that the HTC 16 is on or off. A tool circuiton/off button 484 is also provided to enable the user to electronicallyactivate the active flow control features of the HTC 16. For example,when the user presses the tool circuit on/off button 484 such that thetool control of the HTC 16 is on, as indicated by a corresponding LEDlight 486, the HTC 16 may begin actively controlling the flow ofhydraulic fluid to multiple hydraulic tools, rather than providing thefull hydraulic flow to the auxiliary tool circuit.

In addition to the power on/off button 480 and the tool circuit on/offbutton 484, the faceplate 460 includes a flow/port select button 488.The flow/port select button 488 enables the user to electronically cyclethrough the various operational modes of the HTC 16. The operationalmodes are identified on the faceplate by a series of text indicia 490,492. Each operational mode text indicator is proximate a respective LEDlight 494. In this way, when a given operational mode is selected, theLED light 494 proximate the selected mode is activated. As the userelectronically cycles through the operational modes of the HTC 16, theHTC 16 may adjust the flow to the primary, secondary, or auxiliary tool,or a combination thereof. For example, depending on the selected mode,the HTC 16 may provide an excess flow to a secondary tool, rather thanan auxiliary tool. In another example, the modes of the HTC 16 mayadjust a ratio or split of hydraulic power among multiple tools, such asto the primary, secondary, or auxiliary tool, or a combination thereof.As an example, the ratio or split may be predefined, user programmable,or the like. Indeed, as set forth above, the ratio or split of hydraulicpower among the primary, secondary, and auxiliary tools may berepresented by A:B:C, where A, B, and C each range between 0 to 100, 0to 10, or 0 to 5. In a further example, which may occur in addition toor in lieu of hydraulic output switching, the HTC 16 may directly orindirectly (e.g., via a separate controller) cause a prime mover thatdrives a hydraulic power source to increase or decrease its speed toadjust a total flow of hydraulic fluid provided to the HTC 16 from thehydraulic power source.

The illustrated faceplate 460 also includes text indicia 496 thatprovides information regarding the functionality of one or more of thehydraulic tools while the HTC 16 is in certain modes. Specifically, thetext indicia 496 include a box 498 encompassing certain of the modeindicators with text specifying that the crane, or other auxiliary toolconnected to the HTC 16, is not functional while either of theencompassed modes are activated. For example, the modes encompassed bythe box may correspond to the 10 GPM and 5+5 GPM modes set forth abovein Table 1. As shown in Table 1, the auxiliary tool (e.g., a crane) isnot able to be used in either of these modes if the primary tool is inuse (in the 10 GPM mode) or if the mode is selected (in the 5+5 GPMmode). The faceplate 460 may also include any other combination ofindicia, such as the operability of the secondary hydraulic tool incertain modes, maximum flow rates to certain tools while in certainmodes, and so on.

FIG. 16 illustrates a similar embodiment of a faceplate 500 for the HTC16. The illustrated faceplate 500 includes many of the same features asthe faceplate 460 of FIG. 15, and those features are indicated with thesame reference numerals. The faceplate 500, in addition to or in lieu ofthe button 488 for cycling through the various operational modes of theHTC 16, includes a flow/port select dial 502, which is configured toenable the user to electronically select operational modes of the HTC16. The dial 502 may enable the user to adjust the HTC 16 between flowrates and/or port selections by enabling two-way variability. Forexample, as illustrated, the HTC 16 may be in the 8 GPM mode. Using thedial 502, the user may turn the dial 502 counterclockwise to select the5 GPM mode, or clockwise to select the 10 GPM mode. In some embodiments,these buttons may be used to adjust the flow rate of one or more tools,the ratio or split of hydraulic flow among tools, or the like.

FIG. 17 illustrates another embodiment of a faceplate 510 for the HTC16. The illustrated faceplate 510 includes many of the same features asthe faceplate 460 of FIGS. 15 and 16, and those features are indicatedwith the same reference numerals. The faceplate 510, in addition to orin lieu of the button 488 and/or the dial 502, includes a flow/portselect button set 511. The button set 511 includes a “+” button 512 anda “−” button 514, which are configured to enable the user toelectronically select operational modes of the HTC 16. Each of thebuttons 512, 514 has a respective LED light 516, 518, which areconfigured to provide a visual indication to the user when either of thebuttons are pressed/activated. The button set 511 may enable the user toadjust the HTC 16 between flow rates and/or port selections by enablingtwo-way variability. For example, as illustrated, the HTC 16 may be inthe 8 GPM mode. Using the + button 512, the user may select the 10 GPMmode, and using the − button 514, the user may select the 5 GPM mode. Insome embodiments, these buttons 512, 514 may be used to adjust the flowrate to one or more tools, to adjust the ratio or split of hydraulicflow among various tools, or the like.

While the embodiments set forth in FIGS. 15-17 include text indicia 490,492, 496 and a series of LED lights 494 for indicating the operationalmode selected and various other operational parameters, alternatively oradditionally, other indication features may be used. FIG. 18 illustratesone such embodiment of a faceplate 520 having an electronic readout 522,which may be an LED screen, an LCD screen, a touch panel display, or anysimilar screen capable of generating text and/or symbols. Again, theelectronic readout 522 may be used in addition to or in lieu of thetext/light indications 490, 492, 494, 496 discussed above. Theelectronic readout 522 includes a mode indication 524 and an operationalparameter indication 526. In the illustrated embodiment, the modeindication 524 indicates that the HTC 16 is in 5+5 GPM mode.Accordingly, the operational parameter indication 526 indicates that noauxiliary output is available. The operational parameter indication 526may be used to provide any operational parameter that is germane to theoperation of the HTC 16. For example, when the HTC 16 is in 8 GPM mode,the operational parameter indication 526 may indicate “no secondarytool,” or similar text, indicating that the secondary tool may not beused. The operational parameter indication 526 may also provide certainwarnings, such as an indication that the secondary tool may not be usedwhile the crane is in use. Further, the operational parameter indication526, and other features of the faceplate 510 of FIG. 18 or any of thefaceplates described herein may enable a user to program the amount offlow provided to each hydraulic tool during operation, such as splitratios, modes with associated split ratios, and so forth. Furthermore,such programmability may also enable the user to select priority levelsfor each tool. For example, the user may assign the highest priority tothe auxiliary tool (e.g., the hydraulic crane), with other tools, suchas crimps, drills, saws, etc. being lower priority. The user may alsoinput or adjust threshold pressures, threshold flow rates, or anysimilar input that enables the operation of the HTC 16 to be customizedto the particular use of the end user.

As discussed above with respect to FIG. 8, any one or a combination ofthe hydraulic tools 236, 238, 240 may include a tool control/userinterface that may be in communication with the HTC 16 and/or thecontrol circuit 248. FIG. 19 illustrates an embodiment of one suchhydraulic tool/hydraulic tool control interface 530. Indeed, while theembodiment illustrated in FIG. 19 is described in the context of a userinterface on a hydraulic tool, it should be noted that the interface maybe used as a faceplate or similar interface disposed on or otherwise inoperative connection with the HTC 16. The hydraulic tool/hydraulic toolcontrol interface 530 is configured to enable a user to make electronicadjustments to the HTC 16, calibrate the response of the HTC 16 to theoperation of the hydraulic tool, and monitor flow rates/pressures.Certain of the inputs may have similar functionality to those describedabove for the faceplates of the HTC 16. For example, the interface 530includes a tool circuit on/off button 532, which may have the samefunctionality as the tool circuit on/off button 484 of FIGS. 15-18. AnLED indicator 534 proximate the button 532 is also provided, for exampleto provide a visual indication to the user when the HTC 16 is performingactive output control. The interface also includes a plurality offlow/port select adjustors, which are each configured to enable the userto electronically adjust the operational mode of the HTC 16. Indeed, theinterface 530 includes a flow/port select button 534, a flow/port selectdial 536, and a flow/port select button set 538, which correspond to andperform the same operations as the flow/port select button 488 of FIG.15, the flow/port select dial 502 of FIG. 16, and the flow/port selectbutton set 511 of FIG. 17, respectively.

The interface 530 also includes a tool calibration on/off button 540 andassociated LED indicator 542. The tool calibration on/off button 540enables the user to calibrate certain operational modes of the HTC 16with, for example, a percentage activation of the hydraulic tool towhich the interface 530 is connected. For example, the user may desireto correlate certain operational modes of the HTC 16 with a certainlevel of activation of the hydraulic tool, such as by adjustingthresholds (e.g., pressure thresholds, flow rate thresholds) oradjusting load thresholds corresponding to mode changes. Accordingly,the user is able to change the HTC 16 to a calibration mode or a similarinactive mode by pressing the tool calibration on/off button 540. TheLED indicator 542 then illuminates, which indicates the HTC 16 is in amode where it is able to be calibrated or otherwise programmed and/oradjusted. The user may then cycle through the operational modes and/oroperating thresholds of the HTC 16, which may be viewed by a digitalreadout 544 and/or LED/text indicia 546.

The user may then correlate the selected operational mode and/orselected operating threshold of the HTC 16 with an activation of thehydraulic tool, which may be indicated by a tool activation meter 548and/or a tool activation digital readout 550. In certain embodiments,the tool activation that is displayed may correlate to a percentagetrigger activation of the hydraulic tool. For example, the user maytrigger the tool to a certain extent (e.g., 60%), and correlate theamount of activation of the tool with the selected operational mode ofthe HTC 16.

The interface 530 also includes a user input panel 552, which may be atouchscreen or a keypad. Indeed, in certain embodiments, the user inputpanel 552 includes a plurality of buttons 554, which may be actualbuttons or generated buttons on a touchscreeen. The plurality of buttons554 may each have respective numerals 556 and associated letters 558,which may facilitate the input of certain information relating to theoperation of the HTC 16, various information relating to thecustomization of the HTC 16 or the interface 530, or the like.Generally, the user input panel 552 enables the user to input commands,make adjustments to operational modes, configure personalized readouts,program various modes, and so forth. Furthermore, the user input panel552 may perform any one or a combination of the operations describedabove with regard to the input and monitoring features of the interface530. For example, the user input panel 552 may enable a user to programthe amount of flow provided to each hydraulic tool during operation,such as split ratios, modes with associated split ratios, and so forth.Furthermore, such programmability may also enable the user to selectpriority levels for each tool. For example, the user may assign thehighest priority to the auxiliary tool (e.g., the hydraulic crane), withother tools, such as crimps, drills, saws, etc. being lower priority.The user may also input or adjust threshold pressures, threshold flowrates, or any similar input that enables the operation of the HTC 16 tobe customized to the particular use of the end user. Indeed, theinterface 530 may include any one or a combination of the featuresdescribed herein, as may be determined based on spatial, cost, and/orlogistical constraints.

While only certain features of the invention have been illustrated anddescribed herein, many modifications and changes will occur to thoseskilled in the art. It is, therefore, to be understood that the appendedclaims are intended to cover all such modifications and changes as fallwithin the true spirit of the invention.

1. A system, comprising: a hydraulic supply system, comprising: a drive;a hydraulic pump coupled to the drive; a first hydraulic outputconfigured to supply a first flow of a hydraulic fluid from thehydraulic pump to a hydraulic lift; a second hydraulic output configuredto supply a second flow of the hydraulic fluid from the hydraulic pumpto a first hydraulic tool; and a controller configured to adjust a speedof the drive in response to a feedback indicative of a first load by thehydraulic lift, a second load by the first hydraulic tool, or acombination thereof.
 2. The system of claim 1, wherein the feedbackcomprises a first pressure measurement relating to the first flow, asecond pressure measurement relating to the second flow, or acombination thereof.
 3. The system of claim 1, wherein the feedbackcomprises a first flow rate measurement relating to the first flow, asecond flow rate measurement relating to the second flow, or acombination thereof.
 4. The system of claim 1, wherein the controller isconfigured to increase the speed of the drive if the feedback indicatesan increase in the first or second load, and the controller isconfigured to decrease the speed of the drive if the feedback indicatesa decrease in the first or second load.
 5. The system of claim 1,wherein the controller is configured to adjust the speed of the drive inresponse to a highest load of the first and second loads.
 6. The systemof claim 1, wherein the controller is configured to adjust the speed ofthe drive in response to the feedback in real-time.
 7. The system ofclaim 1, wherein the controller is configured to adjust the speed of thedrive in response to the feedback and at least one relationship betweenthe speed and the first and second loads.
 8. The system of claim 1,wherein the controller is configured to adjust the speed over aplurality of discrete speeds in response to the feedback, and each speedof the plurality of discrete speeds corresponds to a different loadthreshold.
 9. The system of claim 1, wherein the controller isconfigured to continuously vary the speed over a speed range in responseto the feedback.
 10. The system of claim 1, wherein the hydraulic supplysystem comprises a service pack unit having the drive, the hydraulicpump, and the controller.
 11. The system of claim 1, comprising avehicle having the hydraulic supply system and the hydraulic lift,wherein the drive is a main engine of the vehicle or a service engineindependent from the main engine.
 12. A system, comprising: a controllerconfigured to adjust a speed of a drive coupled to a hydraulic pump tochange an output of the hydraulic pump, wherein the controller isconfigured to adjust the speed of the drive in response to a feedbackindicative of a first load by a hydraulic lift configured to receive afirst flow of hydraulic fluid from the hydraulic pump, a second load bya first hydraulic tool configured to receive a second flow of hydraulicfluid from the hydraulic pump, or a combination thereof.
 13. The systemof claim 12, wherein the feedback comprises a first flow ratemeasurement relating to the first flow, a second flow rate measurementrelating to the second flow, or a combination thereof.
 14. The system ofclaim 12, wherein the feedback comprises a first pressure measurementrelating to the first flow, a second pressure measurement relating tothe second flow, or a combination thereof.
 15. The system of claim 12,wherein the controller is configured to increase the speed of the driveif the feedback indicates an increase in the first or second load, andthe controller is configured to decrease the speed of the drive if thefeedback indicates a decrease in the first or second load.
 16. Thesystem of claim 12, comprising a service pack unit having the drive, thehydraulic pump, and the controller.
 17. A system, comprising: a servicepack unit, comprising: a drive; a hydraulic pump coupled to the drive;at least one hydraulic output configured to supply a hydraulic fluidfrom the hydraulic pump to at least one hydraulic tool; and a controllerconfigured to adjust a speed of the drive in response to a feedbackindicative of a load by the at least one hydraulic tool and at least onerelationship between the speed and the load.
 18. The system of claim 17,wherein the at least one relationship comprises a proportionalrelationship between the speed and the load.
 19. The system of claim 17,wherein the controller is configured to adjust the speed over aplurality of discrete speeds in response to the feedback indicative ofthe load, and each speed of the plurality of discrete speeds correspondsto a different load threshold.
 20. The system of claim 17, wherein thecontroller is configured to continuously vary the speed over a speedrange in response to the feedback indicative of the load.